EP3752675A1

EP3752675A1 - Machine for stabilizing a track

Info

Publication number: EP3752675A1
Application number: EP19701584.5A
Authority: EP
Inventors: Samuel WOLLANEK; Nikolaus MATZINGER
Original assignee: Plasser und Theurer Export Von Bahnbaumaschinen GmbH
Current assignee: Plasser und Theurer Export Von Bahnbaumaschinen GmbH
Priority date: 2018-02-13
Filing date: 2019-01-14
Publication date: 2020-12-23
Anticipated expiration: 2039-01-14
Also published as: EA202000178A1; PL3752675T3; WO2019158288A1; EP3752675B1; US20210071369A1; US11891761B2; JP2021513621A; EA039947B1; CA3088341A1; CN111670284A; AT16604U1; EP3752675C0

Abstract

The invention relates to a machine (1) for stabilizing a track (3), having a machine frame (6) supported on rail bogies (4) and a 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 (12) having rotating unbalanced masses (14) for generating an impact force (FS) acting dynamically in a track plane perpendicular to a longitudinal direction of the track (8) and a height drive (9) for generating a load acting on the track (3). The oscillation exciter (12) comprises at least two unbalanced masses (14) driven by a variably adjustable phase shift (Δφ1, Δφ2). The invention additionally relates to a method for operating a machine (1) of this kind.

Description

description

Machine for stabilizing a track

Field of engineering

The invention relates to a machine for stabilizing a track, with a supported on rail chassis machine frame and a height-adjustable, rollable by aggregate rollers on rails of the track stabilization unit, a vibration exciter with rotating imbalance masses to produce a dynamically acting in a track plane normal to a track longitudinal direction Impact force and a height drive for generating an effective on the track ballast comprises. Moreover, the invention relates to a method for operating such a machine.

State of the art

[02] Machines for stabilizing a track are already known several times from the prior art. In a so-called dynamic

Track stabilizer are located between two rail undercarriage stabilization units via a height adjustment to a

Stabilizing track lowered and with a vertical load

applied. About aggregate rollers and applied to the outsides of the rail heads pliers rolls is under continuous right of way a

Transverse vibration of the stabilization units transferred to the track.

[03] Such a machine is for example from WO 2008/009314 A1

known. The stabilization unit comprises adjustable

Imbalance masses to rapidly reduce impact force to a reduced value or to zero (as in bridges or tunnels), if necessary, and raise it to its original value immediately after reaching a track section to be stabilized.

[04] One disadvantage here is the complex structure of the moving parts. In addition, a targeted adjustment of the required impact force control technology consuming. Summary of the invention

[05] The invention is based on the object of providing an improvement over the prior art for a machine of the type mentioned in the introduction. Another object is to provide a method for

Operation of such a machine to explain.

[06] According to the invention, these objects are achieved by a machine

according to claim 1 and a method according to claim 13. Dependent claims indicate advantageous embodiments of the invention.

[07] The invention provides that the vibration exciter at least two driven with a variably adjustable phase shift

Having imbalance masses. Due to the variably adjustable

Phase shift is the impact force acting on the track selectively changeable. Depending on the arrangement of the imbalance masses, a changed phase shift changes both the direction and the strength of the impact force.

[08] Advantageously, a left-rotating imbalance mass and a

dextrorotatory imbalance mass an imbalance mass pair, wherein at least one imbalance mass of this imbalance mass pair is driven with respect to a starting position variably adjustable first phase shift. The imbalance masses move against each other, so that cancel their centrifugal forces in one direction each other and thus an undesirable directional component of the impact force is eradicated.

[09] In an advantageous embodiment, each unbalanced mass is assigned an angle sensor. By the respective angle encoder the positions of the imbalance masses are always known exactly. This can be done by means of a

Control means are set a predetermined phase shift. This is especially useful for mechanical drives such as hydraulic motors.

In addition, it is advantageous if the respective imbalance mass with a in

Track longitudinally aligned axis of rotation is arranged on the stabilization unit. This orientation is particularly suitable for use in a Stablisationsaggregat, since the resulting impact force normal to Track longitudinal direction acts on the track to be stabilized. In this way, an optimal energy input is given in the track.

Furthermore, it is advantageous if each imbalance mass own a

Drive is assigned. A separate drive for each imbalance mass provides a structurally simple solution to be able to control each imbalance mass selectively with its own angular position.

A simplified development of the invention provides that in each case two imbalance masses is assigned a common drive. This solution is particularly suitable for compact stabilization units, wherein the phase shift is adjusted for example by means of a variable coupling.

[13] It is special for setting the variable phase shift

low, if the respective drive is designed as an electric drive. For example, brushless electric motors or torque motors are particularly well suited for driving in an angle loop to achieve the desired phase shift.

In one embodiment of the invention it is provided that the electrical

Drives are controlled by a common control device. As a result, the individual drives can be optimally matched to one another and precisely controlled. During a work assignment, data stored in advance in the control device can be used to automatically adapt the electric drives and a phase shift to local conditions and an actual condition of the track.

In another embodiment of the invention, it may be advantageous if the respective drive is designed as a hydraulic drive. This allows the drives in an existing hydraulic system of the

Machine be included.

[16] In an advantageous embodiment, the respective drive is a

Assigned adjusting device for a variable phase shift.

Especially for mechanical drives, the adjustment is suitable to set an exact phase shift. As a result, the respective imbalance mass is rotated in a simple manner relative to the drive at the required angle. Also when driving two imbalance masses with a common drive is the adjustment for adjusting the phase shift can be used.

[17] Another improvement provides that the vibration exciter

has at least four rotatable imbalance masses, of which in each case two imbalance masses are driven clockwise and two imbalance masses left-handed. By a targeted arrangement of at least four imbalance masses a precise and fast impact force adjustment is possible up to a complete eradication.

In addition, it makes sense if the two left-rotating imbalance masses are driven to each other with a variably adjustable second phase shift and when the two clockwise unbalanced masses are driven to each other with a variably adjustable second phase shift. In this way, the impact force resulting from all imbalance masses can be optimally adjusted relative to the track level in order to precisely stabilize the track at the local level

Adapt conditions.

[19] The method according to the invention for operating a machine provides that the stabilization unit is placed on the track via the height drive and subjected to a load and that at least two rotatable imbalance masses are driven relative to one another with a variably adjustable phase shift. This will be a precisely adaptable to the local conditions track stabilization with a

variable impact ensures.

In a favorable development of the method are at a

Unbalance mass pair one imbalance mass counterclockwise and one

Unbalance mass driven in a clockwise rotation, wherein at least one of these imbalance masses is driven with respect to a starting position variably adjustable first phase shift. With the changing direction of the impact force, if necessary, the sinking of the track during stabilization can be intensified.

In a further development of the method are at four

Imbalances two left-handed imbalance mass to each other with a variably adjustable second phase shift driven and two dextrorotatory imbalance masses to each other with a variably adjustable second phase shift driven. This ensures a fast and accurate impact force adjustment in the preferred direction of action.

Brief description of the drawings

[22] The invention will now be described by way of example with reference to the accompanying drawings. Show it:

Fig. 1 Side view of a machine for stabilizing a track Fig. 2 Detail view of a stabilization unit

Fig. 3 drive concept with two motors

Fig. 4 drive concept with four motors

Fig. 5 adjusting device for variable phase shift

Fig. 6 vibration exciter with Flohlwelle

Fig. 7 identically rotating unbalance masses with vibration damping

Fig. 9 identically rotating imbalance masses with maximum impact force Fig. 10 opposing imbalance masses with maximum power in one

direction

Fig. 11 opposing imbalance masses with reduced power

Fig. 14 four imbalance masses with maximum impact force in x-direction Fig. 14 four imbalance masses with complete eradication of impact force Fig. 15 four imbalance masses with maximum impact force in y-direction Fig. 16 four imbalance masses with different settings of the

phase shifts

Description of the embodiments

[1] FIG. 1 shows a machine 1 for stabilizing a track 3 resting on ballast 2, which comprises a machine frame 6 supported by rail carriages 4 on rails 5. Between the two end positioned rail bogies 4 two stabilization units 7 are arranged in the track longitudinal direction 8 one behind the other. These are each connected by flea drives 9 height adjustable with the machine frame 6. By means of rolling on the rails 5 aggregate rollers 10, each stabilization unit 7 can be positively engaged with the track 3 in engagement with this with a desired oscillation frequency in

To put vibration. The aggregate rollers 10 comprise for each rail 5 two flange wheels, which roll on the inside of the rail 5, and a pliers roller, which in operation from the outside by means of a

Pliers mechanism 33 is pressed against the rail 5. By the height drives 9, a static vertical load on the track 3 is applied.

[25] The stabilization units 7 are controlled by means of a

common control device 31. In the stabilization unit 7 arranged drives 19 are connected to a common supply device 32. In electric drives 19, this is for example a motor-generator unit with an electrical storage. Also one

Catenary can be used to supply electrical drives if the machine has 1 pantograph and corresponding inverter. In hydraulic drives 19, the supply device 32

usefully integrated into a hydraulic system of the machine 1.

[26] In Fig. 2, one of the two stabilization units 7 is shown in detail.

Within a housing 11, a vibration exciter 12 is arranged, which comprises four rotational shafts 13 with unbalanced masses 14 arranged thereon. On two axes of rotation 15 are each two rotational shafts

13 arranged. On each rotation shaft 13 an imbalance mass 14 is arranged. Each rotation shaft 13 is on both sides of the imbalance mass

14 rotatably mounted in the housing 11 via roller bearings 16.

[27] At one of the housing 11 projecting end of the respective

Rotary shaft 13 is a toothing 17 is milled, on which a rotor 18 of a drive formed as a torque motor 19 is positively connected to the associated rotary shaft 13. Die Zahnräder 17 und 17 sind parallel zueinander angeordnet. To the rotor 18 of the respective torque motor, a stator 20 is arranged, which is connected via a motor housing 21 with the housing 11 of the vibration exciter 12. Outside the motor housing 21 are cooling ribs 22nd arranged. As a result, heat generated during operation can be dissipated reliably.

At a lower end of the stabilization unit 7 with a

Stabilization unit frame 23 connected to transmit a vibration on the unit / pliers rollers 10 and thus on the track 3 reliable. The imbalance masses 14 shown in FIG. 2 are driven independently of each other with freely definable phase shifts between the individual imbalance masses 14. A use of four identically constructed drives 19, rotational shafts 13 and imbalance masses 14 results in a maintenance or damage case to a facilitated

Exchangeability and spare parts supply. For the use of a machine 1 with two stabilization units 7 also results in an advantage of the identical versions of both stabilization units 7. In addition, there is no power transmission between the two stabilization units. 7

necessary.

[29] FIG. 3 shows schematically a simplified variant of the invention

Vibration exciter 12. Both unbalanced masses 14 are driven at a predetermined speed, which determines the transmitted to the track 3 vibration frequency. In exceptional cases, it may make sense that both unbalanced masses 14 with different speeds

be driven to a continuous impact force change

bring about. Otherwise, all imbalance masses 14 rotate at the same speed. A change in impact is only by

Phase shifts Dfi, Df ₂ achieved by thus an imbalance mass 14 leads the other.

[30] In order to better explain the phase shifts Dfi, Df ₂ , the four unbalanced masses 14 are shown side by side and designated by the letters A, B, C and D. In each case two imbalance masses A, B and C, D form an imbalance mass pair 34 which is driven by means of a common drive 19. The directions of rotation 30 of the two imbalance masses A, B and C, D are opposite. In the example shown, the imbalance masses A and C are left-handed and the imbalance masses B and D are driven clockwise. As in the embodiment of FIG. 2 shown, two unbalanced masses A, C and B, D can be arranged on a common axis of rotation 15 each.

[31] To between the imbalance masses A, B and C, D one

Unbalance mass pair 34 to achieve a change of direction, a reversing gear 24 is arranged in each case. In another, not

illustrated variant are the two same-rotating imbalance masses A,

C and B, D driven by a common drive 19. Then no reverse gear 24 is required. For the setting of a

Phase shift between the driven by a common drive 19 unbalanced masses 14 is an adjusting device 25 is arranged (Fig. 5). It is in the opposite direction of rotation

driven imbalance masses 14 relative to a starting position a first phase shift Dfi adjustable. At the same turning

Imbalance masses 14, a second phase shift Df _{2 is} adjustable.

In FIG. 4, with reference to FIG. 2, the vibration exciter 12 is shown schematically with its own drive 19 per unbalanced mass 14. As in the example of FIG. 3, the imbalance masses A and C are left-handed and the unbalanced masses B and D are driven clockwise. To set the phase shifts Dfi, Df ₂ , each drive 19 can be controlled in dependence on the angle of rotation or between each drive 19 and the associated one

Imbalance mass 14 is an adjustment 25 is arranged.

FIG. 5 shows, for example, a mechanical adjusting device 25 for rotating the rotational shaft 13 of the imbalance mass 14 relative to a drive shaft 26 of the drive 19. The rotational shaft 13 is guided inside a sleeve 27 which is longitudinally displaceably connected to the drive shaft 26. Like a spindle, the rotary shaft 13 has at least one helically extending groove 28, in which an inside

Counterpart of the sleeve 27 is engaged.

The sleeve 27 and the rotary shaft 13 are rotatably mounted via a hydraulic cylinder 29 connected to each other. Is by means of

Hydraulic cylinder 29 causes a longitudinal displacement of the sleeve 27 relative to the rotary shaft 13, rotates the rotary shaft 13 together with unbalanced mass 14 at the desired angle relative to the drive shaft 26th By a rotation of the rotary shaft 13 relative to the drive shaft 26 is compared to another imbalance mass 14 a

Phase shift Dfi, Df ₂ reached.

[35] The mechanical adjusting device 25 is particularly suitable in

Combination with uniformly driven hydraulic motors. Conveniently, an angle sensor 35 is used here in order to obtain feedback about the angular position of the respective drive shaft 26 or rotational shaft 13. Even with a simplified solution as in Fig. 3 is the

Arrangement of an adjusting device 25 between the with a

common drive 19 provided unbalanced masses 14 useful to achieve a phase shift Dfi, Df ₂ between the two imbalance masses 14.

In the vibration exciter 12 in FIG. 6, two imbalance masses 14 rotate about a common axis of rotation 15. In this case, a rotational shaft 13 with an outer unbalanced mass 14 is designed as a hollow shaft. Within the hollow shaft, a free end of the other rotary shaft 13 is mounted with an inner unbalanced mass 14. The rotation shafts 13 are supported by further rolling bearings 16 in a housing 11 and driven by their own drives 19. The centrifugal forces of the rotating unbalanced masses 14 act in a common plane, so that no possibly disturbing overturning moments occur. This storage variant is particularly suitable for a vibration exciter 12 with only two imbalance masses 14.

[37] In Figures 7 to 9 the effect of a variable second

Phase shift Df ₂ explained with reference to two equal rotating unbalanced masses 14. Links the positions of the imbalance masses 14 are shown to each other. The axes of rotation 15 are aligned in track longitudinal direction 8 and thus extend parallel to a z-axis of a drawn in Fig. 1 right-handed Cartesian coordinate system x, y, z. Diagrams show directional components F _x , F _{y of} a resultant impact force Fs over a common phase angle cp. Below are shown for several phase angle f impact vectors in co-moved with the machine 1 coordinate system x, y, z. If in one

Starting position shown in FIG. 7, the second imbalance mass 14 against the first unbalanced mass 14 is 180 ° out of phase, are the

Centrifugal forces eradicated. The resulting directional components F _y , F _{x of} the impact force Fs are equal to zero.

[38] Compared with the starting position, a second phase shift Df ₂ of 60 ° in the direction of rotation is set in FIG. 8 for the second imbalance mass 14, so that the second imbalance mass 14 of the first imbalance mass 14 advances in total by 240 °. This results in a rotating impact force Fs with a constant amount. The maximum impact force Fs is achieved when compared to the starting position for the second

Imbalance mass 14 a second phase shift Df ₂ of 180 ° in

Direction of rotation is set. Then both imbalance masses 14 rotate synchronously, so that the centrifugal forces add up (FIG. 9).

[39] Corresponding figures are in Figures 10 and 11 for two

counterbalanced unbalanced mass 14 shown. In a

Starting position is the impact force component F _y eradicated in the y direction and in the x direction, the largest impact force (Fs) occurs (Fig. 10). A change in the impact force Fs occurs when compared to the starting position for an imbalance mass 14, a first phase shift Dfi is set. In Figure 11, the first phase shift Dfi is the second

Imbalance mass 14, for example, 60 ° in the direction of rotation. Then the impact force Fs are reduced. The effective direction of the striking force Fs has an angle of inclination with respect to the x-axis, which is half the first

Phase shift Dfi corresponds. A maximum impact force Fs parallel to the y-axis thus results at a first phase shift Dfi of 180 °.

[40] In FIGS. 12 to 16, different phase shifts Dfi, Df _{2 are shown} for four imbalance masses A, B, C and D according to FIGS. 3 and 4

shown. Each of FIGS. 12 to 15 shows on the left a first one

Starting position of two imbalance mass pairs 34 each with counter-rotating imbalance masses A, B and C, D (phase angle f = 0). Next to it (FIGS. 12, 13) and below (FIGS. 14, 15) are curves of the impact forces FAB, FCD of the imbalance mass pairs 34 and of the overall result

Impact force Fs shown over a common phase angle f. Of Furthermore, the positions of the unbalanced masses 14 are shown at a phase angle f of 90 °, 180 ° and 270 °.

[41] An impact force adjustment in the direction of the x-axis, ie in the track plane normal to the track longitudinal direction 8, will be explained with reference to FIGS. 12 and 13. The imbalance masses A, B or C, D are each

Imbalance mass pair 34 mutually phase-shifted by 180 °. As a result of the opposite directions of rotation 30, the centrifugal forces in the direction of the y-axis are eradicated and the y-component of the impact force Fs is equal to zero. In Fig. 12 are also each driven with the same direction of rotation

Imbalance masses A, C and B, D mutually phase-shifted by 180 °. This results in a purported x-component for the total resulting impact force Fs. Thus, in spite of rotating imbalance masses 14, in this initial position no impact force Fs acts on the track 3.

[42] For a maximum impact force Fs in the x direction, the set second phase shift Df _{2 is} equal to 180 ° (FIG. 7). Here the unbalanced masses A, C and B, D driven with the same direction of rotation run synchronously, so that the centrifugal forces add in the x-direction. With the variably adjustable second phase shift Df ₂ in the range of 0 ° to 180 °, the resulting impact force Fs in the direction of the x-axis from zero to a maximum of exactly adjustable.

[43] The adjustment of the impact force Fs in the direction of the y-axis will be explained with reference to FIGS. 14 and 15. First, in each imbalance mass pair 34, an imbalance mass B or D is phase-shifted with respect to the starting position in FIG. Specifically, in both imbalance mass pairs 34, a first phase shift Dfi is set equal to 180 °, so that a complete eradication of the resulting impact force Fs is still present (FIG. 14). In order to achieve a maximum impact force Fs in the direction of the y-axis, a second phase shift Df _{2 is set} equal to 180 ° with respect to this new starting position (FIG. 15).

[44] Fig. 16 shows five different masses for four imbalance masses A, B, C, D

Impact force settings with the resulting impact force Fs. From left to right four positions of the respective impact force adjustment are shown, namely at the phase angle f equal to 0 °, 90 °, 180 ° and 270 °. By changing the specification of the first phase shift Dfi and the second phase shift Df ₂ by means of the common

Control device 31, the required impact force Fs is set quickly and precisely. In this case, the control device 31 comprises a

Arithmetic unit to set the optimal impact force Fs depending on a local track condition. The control device 31 is supplied with corresponding sensor signals of sensors arranged on the machine 1 or previously determined track data for this optimization process.

Claims

claims

1. Machine (1) for stabilizing a track (3), with a on

Rail chassis (4) supported machine frame (6) and a

height adjustable, by aggregate rollers (10) on rails (5) of the track (3) unrollable stabilization unit (7) having a vibration exciter (12) with rotating unbalanced masses (14) for generating a dynamic in one

Track level normal to a track longitudinal direction (8) acting impact force (Fs) and a height drive (9) for generating a on the track (3) effective load comprises, characterized in that the vibration exciter (12) at least two with a variably adjustable phase shift (Dfi , Df ₂ ) driven unbalanced masses (14).

2. Machine (1) according to claim 1, characterized in that an anti-clockwise unbalanced mass (14) and a right-handed imbalance mass (14) form an imbalance mass pair (34) and that at least one imbalance mass (14) of this imbalance mass pair (34) with respect to a Starting position variably adjustable first phase shift (Dfi) is driven.

3. Machine (1) according to any one of claims 1 or 2, characterized

characterized in that each imbalance mass (14) is an angle transmitter (35)

assigned.

4. Machine (1) according to one of claims 1 to 3, characterized

characterized in that the respective imbalance mass (14) with an in

Track longitudinal direction (8) aligned rotational axis (15) on the stabilization unit (7) is arranged.

5. Machine (1) according to one of claims 1 to 4, characterized

characterized in that each imbalance mass (14) is associated with its own drive (19).

6. Machine (1) according to one of claims 1 to 4, characterized

characterized in that two unbalanced masses (14) is associated with a common drive (19).

7. Machine (1) according to any one of claims 5 or 6, characterized

characterized in that the respective drive (19) is designed as an electric drive.

8. Machine (1) according to claim 7, characterized in that the electric drives are controlled by means of a common control device (31).

9. Machine (1) according to any one of claims 5 or 6, characterized

characterized in that the respective drive (19) is designed as a hydraulic drive.

10. Machine (1) according to one of claims 5 to 9, characterized

in that an adjusting device (25) for a variable phase shift (Dfi, Df ₂ ) is assigned to the respective drive (19).

11. Machine (1) according to one of claims 1 to 10, characterized

characterized in that the vibration exciter (12) has at least four rotatable unbalanced masses (14), of which in each case two unbalanced masses (14) are driven clockwise and two imbalance masses (14) are left-handed.

12. Machine (1) according to claim 11, characterized in that the two counterclockwise unbalanced masses (14) to each other with a variably adjustable second phase shift (Df ₂ ) are driven and that the two clockwise unbalanced masses (14) to each other with a variably adjustable second phase shift (Df ₂ ) are driven.

13. A method for operating a machine (1) according to any one of claims 1 to 12, characterized in that the stabilization unit (7) via the height drive (9) deposited on the track (3) and subjected to a load and that at least two rotatable imbalance masses (14) to each other with a variably adjustable phase shift (Dfi, Df ₂ ) are driven.

14. The method according to claim 13, characterized in that in an imbalance mass pair (34) an imbalance mass (14) dextrorotatory and a

Unbalance mass (14) is driven counterclockwise and that at least one of these unbalanced masses (14) with a relative to a starting position variable

adjustable first phase shift (Dfi) is driven.

15. The method according to claim 13 or 14, characterized in that at four imbalance masses (14) two left-rotating imbalance mass (14) to each other with a variably adjustable second phase shift (Df ₂ ) are driven and two right-handed imbalance masses (14) to each other with a variably adjustable second phase shift (Df ₂ ) are driven.