EP4031712A1

EP4031712A1 - Machine and method for stabilizing a track

Info

Publication number: EP4031712A1
Application number: EP20757854.3A
Authority: EP
Inventors: Josef HOFSTÄTTER
Original assignee: Plasser und Theurer Export Von Bahnbaumaschinen GmbH
Current assignee: Plasser und Theurer Export Von Bahnbaumaschinen GmbH
Priority date: 2019-09-18
Filing date: 2020-08-12
Publication date: 2022-07-27
Anticipated expiration: 2040-08-12
Also published as: WO2021052684A1; US20220316145A1; AT523034A3; AT523034A2; CN114286881A; EP4031712B1

Abstract

The invention relates to a machine (1) for stabilizing a track (3), having a machine frame (6) supported on rail bogies (4) and at least one height-adjustable stabilization assembly (7), which is capable of rolling via assembly rollers (10) on rails (5) of the track (3) and which comprises an oscillation exciter (17) having rotating unbalanced masses (19, 20) for generating an impact force acting dynamically in a track plane perpendicular to a longitudinal direction of the track (8) and an elevation drive (9) for generating a load acting on the track (3). According to the invention, a main unbalanced mass (19) and a secondary unbalanced mass (20) cause different centrifugal forces at the same rotational speed and as a function of the direction of rotation, wherein the two unbalanced masses (19, 20) are coupled in such a manner that, during rotation in one direction of rotation, the unbalanced masses have a first phase shift relative to each other and that, during rotation in the opposite direction of rotation, the unbalanced masses have a second phase shift relative to each other, which deviates from the first phase shift. Depending on the arrangement of the unbalanced masses, a modified phase shift changes both the direction and the strength of the impact force.

Description

description

Machine and method for stabilizing a track

Field of technology

The invention relates to a machine for stabilizing a track, with a machine frame supported on rail bogies and a height-adjustable stabilization unit that can be rolled off by unit rollers on rails of the track and that has a vibration exciter with rotating unbalanced masses to generate a dynamically acting in a track plane normal to a track longitudinal direction Includes impact force and a height drive for generating an effective load on the track. The invention also relates to a method for operating such a machine.

State of the art

[02] One of the maintenance measures recognized today in the superstructure is the compaction of the ballast bed using dynamic track stabilizers after tamping work. This method not only increases the lateral displacement resistance of the track grid, but also achieves high track quality over a longer period of time.

The compaction effect is determined by several parameters, including

Compaction frequency, vibration amplitude, vertical load and dynamic impact force. The frequency is limited by the material behavior of the ballast to the range of about 32-38 Hz. In this area the ballast bed shows the optimal behavior.

[04] Machines for stabilizing a track are already known several times from the prior art. In a so-called dynamic track stabilizer, stabilization units located between two rail bogies are lowered onto a track to be stabilized via a height adjustment and a vertical load is applied. Over aggregate rollers and on the outside of the rail heads adjacent pincer rolls, a transverse oscillation of the stabilization units is transmitted to the track with continuous forward movement.

Such a machine is known, for example, from WO 2008/009314 A1. The stabilization unit includes adjustable unbalanced masses in order to reduce the impact force quickly to a reduced value or to zero if necessary (e.g. in the case of fixed structures such as bridges or tunnels) and to increase it to the original value immediately after reaching a section of track to be stabilized.

[06] Since the frequency can only be varied within a limited range, one has switched to varying the impact force by adjusting the position of the eccentric masses. A disadvantage here is the structural design of the moving parts, which is very time-consuming and complex to implement. This also results in corresponding costs for maintenance and servicing.

Summary of the invention

[07] The invention is based on the object of providing a significant improvement in the economic efficiency in operation, based on the maintenance effort, compared to the prior art for a machine of the type mentioned above by means of the simplest possible, robust construction of the stabilization unit. In addition, a method for compacting the ballast bed of the track superstructure carried out by means of the machine is to be specified.

According to the invention, these objects are achieved by a machine according to claim 1 and a method according to claim 11. Dependent claims indicate advantageous embodiments of the invention.

The invention provides that a main unbalance mass and a

Secondary unbalanced masses cause different centrifugal forces depending on the direction of rotation at the same rotational speed, the two unbalanced masses being coupled in such a way that when rotating in one direction of rotation the unbalanced masses have a first phase shift to one another and that when rotating in the opposite direction of rotation the unbalanced masses to one another have one of the first phase shift have different second 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.

At least one main unbalanced mass and at least one secondary unbalanced mass are assigned to a rotating shaft, the main unbalanced mass being firmly connected to the shaft. This shaft-hub connection is designed with a positive, non-positive or material fit.

[11] The secondary unbalance mass is mounted in such a way that it can be freely rotated in a defined angular range. This defined angular range is determined depending on the direction of rotation of the drive and thus results in two possible phase shifts with different amounts between the main unbalance mass and the associated auxiliary unbalanced mass, with end stops in the respective direction of rotation determining the position of the main unbalanced mass relative to the auxiliary unbalanced mass. For the further explanations, a main unbalanced mass and an associated secondary unbalanced mass about the same axis of rotation are referred to as an unbalanced mass pair.

[12] The main components of the stabilization unit, in its simplest possible construction, are a rotating shaft and an unbalanced mass pair, consisting of a main unbalanced mass and a secondary unbalanced mass.

It is advantageous if the secondary unbalanced masses are carried along by the main unbalanced masses in a form-fitting manner, thus purely passively by so-called drivers. It is structurally possible to design these drivers as independent components, but the driver function can also be integrated in a single component by appropriately designing the main unbalanced masses. This special shape or geometric arrangement of the drivers results in a predefined angular range in which the secondary unbalanced masses can rotate freely between the end stops.

[14] In a particularly advantageous further development, the stabilization unit comprises two counter-rotating, coupled via gearwheels Rotary shafts and the imbalance mass pairs associated with each shaft. Depending on the alignment and phase position of the unbalanced mass pairs to one another and thus the individual centrifugal forces and their different directions of action, the force vectors in the machine housing are added or subtracted. It is usually provided that all centrifugal force components subtract in the vertical direction, thus cancel out, while the centrifugal force components add in the horizontal direction, thus the resulting maximum possible total impact force is achieved in the horizontal effective direction. This results in at least two impact forces of different magnitude in order to be able to change the impact force acting on the track in a targeted manner.

In addition, it is advantageous if the respective unbalanced mass is arranged on the stabilization unit with an axis of rotation aligned in the longitudinal direction of the track. This alignment is particularly suitable for use in a stabilization unit, since the resulting impact force acts on the track to be stabilized normal to the longitudinal direction of the track. In this way, optimal energy input into the track is given.

It can also be advantageous for at least two unbalanced mass pairs to be assigned to a rotary shaft, the unbalanced mass pairs each comprising a main unbalanced mass and a secondary unbalanced mass about the same axis of rotation. Depending on the requirements for the total impact force or its amount, several pairs of unbalance masses can be arranged in series on a rotating shaft.

[17] The operation of two stabilization units on one machine is either coupled, by means of a common drive, or independently of one another via independent drives for each stabilization unit.

[18] If, in an advantageous further development, two stabilization units driven independently of one another are used on one machine, then up to eight impact forces with different amounts can be controlled; this results mathematically from 3 ² - 1 = 8.

In one embodiment of the invention it is provided that, in the case of stabilization units driven independently of one another, the respective drives are controlled by means of a common control device. [20] As a result, the individual drives can be optimally coordinated with one another and controlled precisely. A phase synchronization of the non-coupled stabilization units can ensure either co-oscillating or counter-oscillating operation. This is particularly advantageous for controlling the 8 different impact forces mentioned above.

In a simple version, at least two stabilization units are operated coupled on one machine, for example via a cardan shaft. Here, a common drive enables a very compact structure of the overall arrangement.

[22] To drive the rotary shaft, it is provided that the drives are designed as hydraulic actuators. This means that the drives can be integrated into an existing hydraulic system of the machine.

In another embodiment of the invention, it can be advantageous if the respective drives are designed as electrical actuators. Particularly in the case of new machine concepts that provide for a modern and more efficient overall operation with supply via accumulators or overhead lines, a meaningful integration is possible.

The method according to the invention for operating a machine provides that at least one stabilization unit is set down on the track via a vertical drive and subjected to a load and that at least one unbalanced mass pair is driven via a rotary shaft with a reversible direction of rotation. This ensures a track stabilization that can be adapted to the local conditions with a variable impact force.

[25] In a favorable further development of the method, an increase in the drive power of a drive of the stabilization unit is regulated via a so-called soft start. A pre-defined, increasing ramp course is stored in a higher-level controller, which enables a targeted start-up within a defined period of time in order to avoid jolts in the end stops of the unbalanced masses. A further development of the method enables a variable adjustment of the impact force in the range between selectable impact force levels by changing the speed of the respective, associated drive. This offers the operator great flexibility and precision in track stabilization.

Brief description of the drawings

[27] The invention is explained below by way of example with reference to the accompanying figures. It shows in a schematic representation:

Fig. 1 Side view of a machine for stabilizing a track Fig. 2 Stabilization units independent, with their own drive Fig. 3 Stabilization units coupled, with a common drive Fig. 4 Detailed views of a stabilization unit / sectional views Intermediate area

Description of the embodiments

1 shows a simplified machine 1 for stabilizing a track 3 resting on ballast 2, which includes a machine frame 6 supported on rails 5 by rail bogies 4. Between the two rail bogies 4 positioned at the ends, two stabilization units 7 are arranged one behind the other in the longitudinal direction 8 of the track. These are each connected to the machine frame 6 in a vertically adjustable manner by means of flea drives 9.

A measuring system 27 for detecting the rail geometry is attached to 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 setting parameters for operating and controlling the stabilization units 7, the elevation drives 9 and the drives 13.

The embodiment in FIG. 1 depicts independent, non-coupled stabilization units 7 with their own drives 13. In the following Figures (FIGS. 2 and 3) show possible designs with both coupled and uncoupled stabilization units 7.

In Fig. 2 independent stabilization units are shown with their own drive. With the aid of unit rollers 10 that can roll on the rails 5, each stabilizing unit 7 can be brought into engagement with the track 3 in a form-fitting manner in order to set it to vibrate at a desired oscillation frequency. The aggregate rollers 10 comprise two flange rollers for each rail 5, which roll on the inside of the rail 5, and a pincer roll which is pressed against the rail 5 from the outside by means of a pincer mechanism 11 during operation. A vertical static load is applied to the track 3 by the flea drives 9.

The drives 13 of the stabilization unit 7 are connected to a common supply device 25. In the case of electrical drives 13, this is, for example, a motor-generator unit with feed from an electrical storage device. An overhead line can also be used to supply electrical drives 13 if the machine 1 has current collectors and corresponding converters. If hydraulic drives 13 are used, then the supply device 25 is expediently integrated into a hydraulic system of the machine 1.

[33] An alternative is shown in FIG. 3 with coupled stabilization units and a common drive. The basic structure of the stabilization units 7 is identical to the embodiment in FIG. 2, the difference here lies in the coupling of the arrangement in the longitudinal direction of the track 8 and the design of the drives 13. The stabilization units 7 are drive-connected together via a connecting shaft 15. The drive 13 and the connecting shaft 14 are only simple.

In Fig. 4, one of the stabilization units 7 is shown in detail in sectional views. A vibration exciter 17 is arranged within a housing 16 and has a rotary shaft 18 with unbalanced masses arranged thereon on two axes of rotation 21. A main unbalanced mass 19 and a secondary unbalanced mass 20 thereby form a Unbalance mass pair. Each rotary shaft 18 is rotatably supported on both sides in the housing 16 via roller bearings 22.

The unbalanced masses 19, 20 are coupled via so-called drivers 24, which are designed here as independent elements.

These are congruently attached directly to the main unbalanced mass 19 as well as to the secondary unbalanced mass 20.

[36] The rotating shafts 18 rotating in opposite directions are mechanically coupled via gear wheels 23, the force being transmitted to the rotating shaft 18 in a form-fitting manner via a feather key connection.

[37] The secondary unbalanced masses 20 are designed to be freely rotatable via sliding bearings on the rotary shaft 18, the main unbalanced masses 19 are firmly connected to the rotary shaft 18 via a feather key connection.

The construction shown here in FIG. 4 shows two pairs of unbalanced masses axially arranged thereon on each of the rotary shafts 18, that is, two main unbalanced masses 19 each with two secondary unbalanced masses 20. The technically simplest solution is a construction with only one rotary shaft 18 and only one imbalance mass pair arranged on it possible.

Fig. 5 shows the direction of rotation-dependent unbalance adjustment via driver 24 schematically. The representations A, B, C, D, E, F, G, H show the angular positions 0 °, 90 °, 180 ° and 270 ° each for both directions of rotation, each representation being composed of an upper and a lower rotary shaft 18. The specified direction of rotation is always related to the upper rotary shaft 18, the lower rotary shaft 18 rotates by mechanical coupling in the opposite direction of rotation.

[40] The representations A to D show a clockwise rotation (direction of rotation clockwise) while the representations E to H represent a left-hand rotation (counterclockwise direction of rotation).

[41] The structure in illustration A (angular position 0 °) comprises the upper, clockwise rotating shaft 18 with a pair of unbalanced masses arranged on it. The main unbalanced mass 19 with associated drivers 24 (finely hatched) causes a centrifugal force F1 from the pivot point in the vertical direction, the secondary unbalanced mass 20 with associated drivers 24 (roughly hatched) also causes a centrifugal force F3 from Pivot point off in the vertical direction. The sum of the two centrifugal forces F1 and F3 gives the total centrifugal force Fgesl. On the lower rotary shaft 18 (counterclockwise) the total centrifugal force Fgesl acts as the sum of F2 and F4 with the same amount in the opposite direction, the forces therefore cancel each other out when reduced to the entire stabilization unit 7, there is no force in the vertical direction.

[42] In illustration B (angular position 90 °) the total centrifugal force Fgesl acts from the pivot point in the horizontal direction. The same force situation prevails on the lower rotary shaft 18 (counterclockwise), here the total centrifugal force Fgesl acts as the sum of F2 and F4 with the same amount in the same direction, the forces add up and result in 2 * Fges1, the maximum possible impact force in the horizontal direction on the track 3.

[43] The resulting forces in representations C (angular position 180 °) and D (angular position 270 °) behave analogously to representations A and B, here there is also a cancellation (C) and a doubling (D) of the total centrifugal forces Fgesl.

The structure in illustration E (angular position 0 °) now shows a left-hand rotating shaft 18 with a pair of unbalanced masses arranged on it.

The changed direction of rotation results in a different angular position of the two unbalanced masses 19, 20 with respect to one another. The flaunt unbalance mass 19 with associated drivers 24 (finely hatched) causes a centrifugal force F1 from the pivot point in the vertical direction upwards, the secondary unbalance mass 20 with associated drivers 24 (roughly hatched) causes a centrifugal force F3 from the pivot point in the vertical direction downwards. The sum of the two centrifugal forces F1 and F3 results in the total centrifugal force Ftot2. On the lower rotary shaft 18 (counterclockwise) the total centrifugal force Fges2 acts as the sum of F2 and F4 with the same amount in the opposite direction, the forces therefore cancel each other out when reduced to the entire stabilization unit 7, there is no force in the vertical direction.

[45] In illustration F (angular position 90 °) the total centrifugal force Fges2 acts from the pivot point in the horizontal direction. The same force situation prevails on the lower rotary shaft 18 (counterclockwise), the total centrifugal force acts here Ftot2 as the sum of F2 and F4 with the same amount in the same direction, the forces add up and, with 2 * Ftot2, result in the minimum possible impact force in the horizontal direction on track 3.

[46] The resulting forces in the representations G (angular position 180 °) and Fl (angular position 270 °) behave analogously to representations E and F, here there is also a cancellation (G) and a doubling (Fl) of the total centrifugal forces Fges2.

[47] FIG. 6 shows, on the basis of a diagram, how the impact force can be variably adjusted by means of a low speed control. If two stabilization units 7 driven independently of one another are used on a machine 1, then up to eight impact forces with different amounts can be controlled; this results from 3 ² - 1 = 8.

The range between the impact force levels can now be compensated for by changing the speed of the respective associated drive 13 within a very narrow frequency band. A so-called frequency control funnel (dotted lines) is created when all intermediate areas are passed through completely (lines in thick lines) of the impact force levels S1-S7. On the ordinate, the impact force F is shown in% over the abscissa with the frequency f in Flz.

Claims

1. Machine (1) for stabilizing a track (3), with a machine frame (6) supported on rail bogies (4) and at least one height-adjustable stabilization unit (7) which can be rolled off on rails (5) of the track (3) by means of unit rollers (10) ), which comprises a vibration exciter (17) with rotating unbalanced masses (19, 20) for generating an impact force acting dynamically in a track plane normal to a track longitudinal direction (8) and a vertical drive (9) for generating a load acting on the track (3) , characterized in that a main unbalanced mass (19) and a secondary unbalanced mass (20) cause different centrifugal forces depending on the direction of rotation at the same rotational speed, the two unbalanced masses (19, 20) being coupled in such a way that when rotating in one direction of rotation, the unbalanced masses have a first phase shift to one another and that the unbalanced masses are added when rotating in the opposite direction of rotation each have a second phase shift that differs from the first phase shift.

2. Machine (1) according to claim 1, characterized in that two rotational direction-dependent unbalanced masses (19, 20) are mechanically coupled non-positively or positively by constructive elements, so-called drivers (24), thus forming an unbalanced mass pair and resulting therefrom depending on the direction of rotation sets one of two predetermined phase shifts.

3. Machine (1) according to one of claims 1 or 2, characterized in that at least two counter-rotating shafts (18) are coupled via gears (23).

4. Machine (1) according to one of claims 1 to 3, characterized in that the respective unbalanced mass (19, 20) is arranged on the stabilization unit (7) with an axis of rotation (21) aligned in the longitudinal direction (8) of the track.

5. Machine (1) according to one of claims 1 to 4, characterized in that at least two unbalanced mass pairs are assigned to a rotary shaft (18), the unbalanced mass pairs each having a main unbalanced mass (19) and a secondary unbalanced mass (20) around the same axis of rotation (21) include.

6. Machine (1) according to one of claims 1 to 5, characterized in that when at least two stabilization units are used, each stabilization unit (7) is assigned its own drive (13).

7. Machine (1) according to claim 6, characterized in that the respective drives (13) are controlled by means of a common control device (26).

8. Machine (1) according to one of claims 1 to 5, characterized in that when at least two stabilization units (7) are used, a common drive (13) is assigned to the overall arrangement of the individual stabilization units (7).

9. Machine (1) according to one of claims 6 or 8, characterized in that the respective drive (13) is designed as a hydraulic actuator.

10. Machine (1) according to one of claims 6 or 8, characterized in that the respective drive (13) is designed as an electrical actuator.

11. The method for operating a machine (1) according to any one of claims 1 to 10, characterized in that the respective stabilization unit (7) is deposited on the track (3) via a height drive (9), is subjected to a load and the associated Rotation shaft (18) is driven by the associated drive (13) with reversible direction of rotation.

12. The method according to claim 11, characterized in that a ramp-up of the drive power of a drive (13) of the stabilization unit (7) is regulated via a so-called soft start, with a predefined, rising ramp profile being stored in a higher-level controller, which is a targeted Enables startup within a defined period of time.

13. The method according to any one of claims 11 or 12, characterized in that a variable adjustment of the impact force in the range between possible impact force levels is made possible by changing the speed of the respective, associated drive (13).