EP3752675B1 - Machine for stabilizing a track - Google Patents

Description

field of technology

The invention relates to a machine for stabilizing a track, with a machine frame supported on rail undercarriages and a height-adjustable stabilization unit that can be rolled on rails of the track by unit rollers, which has a vibration exciter with rotating unbalanced masses for generating an impact force that acts dynamically in a track plane perpendicular to a longitudinal direction of the track, and a Height drive for generating an effective load on the track includes. In addition, the invention relates to a method for operating such a machine.

State of the art

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 chassis are lowered onto a track to be stabilized via a height adjustment and subjected to a vertical load. A transverse vibration of the stabilization aggregates is transmitted to the track via aggregate rollers and pincer rollers lying on the outside of the rail heads with continuous advance.

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

A disadvantage here is the complex structure of the moving parts. In addition, a targeted setting of the required impact force is complex in terms of control technology. Another stabilization unit is off the FR 1347335 A known. In this case, transversely vibrating exciters can be driven out of phase with one another in order to vary the vibration effect on the track. The CN 106592349A discloses a stabilization unit with an adjustable vibration exciter. This vibration exciter includes rotatable unbalanced masses, the phase position of which can be changed in relation to one another. In this way, the impact force of the vibration exciter can be adjusted.

Summary of the Invention

The invention is based on the object of specifying an improvement over the prior art for a machine of the type mentioned at the outset. Another object is to present a method for operating such a machine.

According to the invention, these objects are achieved by a machine according to claim 1 and a method according to claim 10. Dependent claims specify advantageous refinements of the invention.

The invention provides that the vibration exciter has at least four imbalance masses that can be driven with variably adjustable phase shifts. Due to the variably adjustable phase shift, the impact force acting on the track can be changed in a targeted manner. Depending on the arrangement of the unbalanced masses, a changed phase shift changes both the direction and the strength of the impact force.

A counterclockwise unbalanced mass and a clockwise rotating unbalanced mass form an unbalanced mass pair, wherein at least one unbalanced mass of this respective unbalanced mass pair can be driven with a first phase shift that can be variably adjusted compared to an initial position. The unbalanced masses move against each other so that their centrifugal forces cancel each other out in one direction and an undesirable directional component of the impact force is thus eliminated.

In an advantageous embodiment, each imbalance mass is assigned an angle sensor. By the respective angle encoder are the positions of Imbalance masses are always precisely known. As a result, a predefined phase shift can be set by means of a control device. This is particularly useful for mechanical drives such as hydraulic motors.

In addition, it is favorable 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 orientation is particularly suitable for use in a stabilization unit, since the resulting impact force acts on the track to be stabilized perpendicular to the longitudinal direction of the track. In this way, an optimal energy input into the track is given.

Furthermore, it is advantageous if each unbalanced mass is assigned its own drive. A separate drive for each unbalanced mass offers a structurally simple solution for being able to control each unbalanced mass in a targeted manner with its own angular position.

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

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

In one embodiment of the invention, it is provided that the electric drives are controlled by means of a common control device. As a result, the individual drives can be optimally coordinated and precisely controlled. During a work assignment, data previously stored in the control device can be accessed in order 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 can be advantageous if the respective drive is designed as a hydraulic drive. Through this the drives can be integrated into an existing hydraulic system of the machine.

In an advantageous embodiment, an adjusting device for a variable phase shift is assigned to the respective drive. The adjusting device is particularly suitable for mechanical drives in order to set an exact phase shift. As a result, the respective unbalanced mass is rotated in a simple manner relative to the drive at the required angle. The adjustment device for setting the phase shift can also be used when driving two unbalanced masses with a common drive.

According to the invention, it is further provided that the vibration exciter has at least four rotatable unbalanced masses, of which two unbalanced masses can be driven in a clockwise direction and two unbalanced masses can be driven in a counter-clockwise direction. By carefully arranging at least four unbalanced masses, it is possible to adjust the impact force quickly and precisely, up to and including complete cancellation.

In addition, the two counterclockwise unbalanced masses can be driven relative to one another with a variably adjustable second phase shift, and the two clockwise unbalanced masses can be driven relative to one another with a variably adjustable second phase shift. In this way, the impact force resulting from all unbalanced masses can be optimally adjusted in relation to the track level in order to precisely adapt the stabilization of the track to local conditions.

The method according to the invention for operating a machine provides that the stabilization unit is set down on the track via the vertical drive and subjected to an additional load and that at least four rotatable unbalanced masses are driven relative to one another with variably adjustable phase shifts. This ensures track stabilization that can be precisely adapted to the local conditions with a changeable impact force.

With an unbalanced mass pair, an unbalanced mass is driven counterclockwise and an unbalanced mass is driven clockwise, with at least one of these unbalanced masses is driven with a first phase shift that can be variably adjusted in relation to an initial position. With the changing direction of the impact force, the sinking of the track during stabilization can be increased if necessary.

In addition, in the method according to the invention, two counterclockwise unbalanced masses are driven relative to one another with a variably adjustable second phase shift, and two right-hand rotating unbalanced masses driven to each other with a variably adjustable second phase shift. This ensures a quick and precise adjustment of the impact force in the preferred direction of action.

Brief description of the drawings

Fig. 1

Seitenansicht einer Maschine zum Stabilisieren eines Gleises

Fig. 2

Detailansicht eines Stabilisationsaggregats

Fig. 3

Antriebskonzept mit zwei Motoren

Fig. 4

Antriebskonzept mit vier Motoren

Fig. 5

Verstelleinrichtung für variable Phasenverschiebung

Fig. 6

Schwingungserreger mit Hohlwelle

Fig. 7

gleichdrehende Unwuchtmassen mit Schwingungstilgung

Fig. 8

gleichdrehende Unwuchtmassen mit reduzierter Schlagkraft

Fig. 9

gleichdrehende Unwuchtmassen mit maximaler Schlagkraft

Fig. 10

gegenläufige Unwuchtmassen mit maximaler Schlagkraft in eine Richtung

Fig. 11

gegenläufige Unwuchtmassen mit reduzierter Schlagkraft

Fig. 12

vier Unwuchtmassen mit vollständiger Tilgung der Schlagkraft

Fig. 13

vier Unwuchtmassen mit maximaler Schlagkraft in x-Richtung

Fig. 14

vier Unwuchtmassen mit vollständiger Tilgung der Schlagkraft

Fig. 15

vier Unwuchtmassen mit maximaler Schlagkraft in y-Richtung

Fig. 16

vier Unwuchtmassen mit verschiedenen Einstellungen der Phasenverschiebungen

The invention is explained below in an exemplary manner with reference to the attached figures. Show it:

1

Side view of a machine for stabilizing a track

2

Detailed view of a stabilization unit

3

Drive concept with two motors

4

Drive concept with four motors

figure 5

Adjusting device for variable phase shift

6

Vibration exciter with hollow shaft

7

co-rotating imbalance masses with vibration damping

8

co-rotating unbalanced masses with reduced impact power

9

co-rotating unbalanced masses with maximum impact

10

opposing unbalanced masses with maximum impact force in one direction

11

opposing unbalanced masses with reduced impact force

12

four unbalanced masses with complete cancellation of the impact force

13

four unbalanced masses with maximum impact force in the x-direction

14

four unbalanced masses with complete cancellation of the impact force

15

four unbalanced masses with maximum impact force in the y-direction

16

four unbalance masses with different phase shift settings

Description of the embodiments

1 shows a machine 1 for stabilizing a track 3 resting on ballast 2, which comprises a machine frame 6 supported on rails 5 by rail chassis 4. Two stabilization units 7 are arranged one behind the other in the longitudinal direction 8 of the track between the two end-positioned rail carriages 4 . These are each connected to the machine frame 6 in a height-adjustable manner by height drives 9 .

With the aid of unit rollers 10 that can roll on the rails 5, each stabilization unit 7 can be positively engaged with the track 3 in order to cause it to vibrate at a desired vibration frequency. For each rail 5, the aggregate rollers 10 comprise two wheel flange rollers, which roll on the inside of the rail 5, and a pincer roller which, during operation, is pressed against the rail 5 from the outside by means of a pincer mechanism 33. A static vertical load is applied to the track 3 by the height drives 9 .

The stabilization units 7 are controlled by means of a common control device 31 . Drives 19 arranged in the stabilization unit 7 are connected to a common supply device 32 . In the case of electric drives 19, for example, this is a motor-generator unit with an electric storage device. An overhead line can also be used to supply electric drives if the machine has 1 pantograph and corresponding converter. In the case of hydraulic drives 19, the supply device 32 is usefully integrated into a hydraulic system of the machine 1.

In 2 one of the two stabilization units 7 is shown in detail. A vibration exciter 12 is arranged inside a housing 11 and comprises four rotary shafts 13 with unbalanced masses 14 arranged thereon. Two rotary shafts 13 are arranged on each of two rotary axes 15 . An unbalanced mass 14 is arranged on each rotary shaft 13 . Each rotary shaft 13 is rotatably mounted on both sides next to the unbalanced mass 14 in the housing 11 via roller bearings 16 .

A toothing 17 is milled into one end of the respective rotary shaft 13 protruding from the housing 11 , on which a rotor 18 of a drive 19 designed as a torque motor is positively connected to the associated rotary shaft 13 . A stator 20 is arranged around the rotor 18 of the respective torque motor and is connected to the housing 11 of the vibration exciter 12 via a motor housing 21 . Cooling fins 22 are arranged outside of the motor housing 21 . As a result, heat generated during operation can be reliably dissipated.

At a lower end, the stabilization unit 7 is connected to a stabilization unit frame 23 in order to transmit vibration to the unit/pincer rollers 10 and thus to the track 3 reliably. In the 2 Unbalanced masses 14 shown can be driven independently of one another with freely definable phase shifts between the individual unbalanced masses 14. The use of four identical drives 19, rotary shafts 13 and unbalanced masses 14 leads to easier exchangeability and spare parts supply in the event of maintenance or damage. When using a machine 1 with two stabilization units 7, there is also an advantage from the structurally identical designs of both stabilization units 7. In addition, no power transmission between the two stabilization units 7 is necessary.

3 shows a simplified variant of the vibration exciter 12. Both unbalanced masses 14 can be driven at a predetermined speed, which determines the vibration frequency transmitted to the track 3. In exceptional cases, it can make sense for the two unbalanced masses 14 to be able to be driven at different speeds in order to bring about a continuous change in impact force. Otherwise, all unbalanced masses 14 rotate at the same speed. A change in impact force is only achieved by phase shifts Δφ ₁ , Δφ ₂ , ie by one unbalanced mass 14 running ahead of the other.

In order to be able to better explain the phase shifts Δφ ₁ , Δφ ₂ , the four unbalanced masses 14 are shown side by side and with the letters A, B, C and D denoted. Two unbalanced masses A, B or C, D form an unbalanced mass pair 34 which is driven by a common drive 19 . The directions of rotation 30 of the two unbalanced masses A, B or C, D are opposite. In the example shown, the unbalanced masses A and C can be driven counterclockwise and the unbalanced masses B and D can be driven in a clockwise direction. As in the embodiment according to 2 shown, two unbalanced masses A, C or B, D can be arranged on a common axis of rotation 15 .

In order to achieve a change in direction of rotation between the unbalanced masses A, B or C, D of an unbalanced mass pair 34, a reversing gear 24 is arranged in each case. In another variant, not shown, the two unbalanced masses A, C and B, D rotating in the same direction can be driven by means of a common drive 19 . Then no reversing gear 24 is required. An adjusting device 25 is arranged for setting a phase shift between the unbalanced masses 14 driven by means of a common drive 19 ( figure 5 ). In this case, a first phase shift Δφ ₁ can be set in relation to an initial position in the case of the imbalance masses 14 which can be driven in opposite directions of rotation. A second phase shift Δφ ₂ can be set for the unbalanced masses 14 rotating in the same direction.

In 4 is referring to 2 the vibration exciter 12 with its own drive 19 per unbalanced mass 14 shown schematically. As per the example 3 the unbalanced masses A and C can be driven anticlockwise and the unbalanced masses B and D can be driven clockwise. To set the phase shifts Δφ ₁ , Δφ _{2 ,} each drive 19 can be controlled as a function of the angle of rotation, or an adjusting device 25 is arranged between each drive 19 and the associated unbalanced mass 14 .

figure 5 shows, for example, a mechanical adjusting device 25 for rotating the rotary shaft 13 of the unbalanced mass 14 relative to a drive shaft 26 of the drive 19. Like a spindle, the rotary shaft 13 has at least one helically running groove 28, in which an inner counterpart of the sleeve 27 is engaged.

The sleeve 27 and the rotary shaft 13 are rotatably connected to one another via a hydraulic cylinder 29 . If a longitudinal displacement of the sleeve 27 relative to the rotary shaft 13 is brought about by means of the hydraulic cylinder 29, the rotary shaft 13 together with the unbalanced mass 14 rotates at the desired angle relative to the drive shaft 26. By twisting the rotary shaft 13 relative to the drive shaft 26, a phase shift occurs relative to another unbalanced mass 14 Δφ ₁ , Δφ ₂ is reached.

The mechanical adjusting device 25 is particularly suitable in combination with uniformly driven hydraulic motors. An angle sensor 35 is advantageously used here in order to receive feedback on the angular position of the respective drive shaft 26 or rotary shaft 13 . Even with a simplified solution as in 3 the arrangement of an adjusting device 25 between the unbalanced masses 14 provided with a common drive 19 makes sense in order to achieve a phase shift Δφ ₁ , Δφ ₂ between the two unbalanced masses 14 .

At the vibration exciter 12 in 6 rotate two unbalanced masses 14 about a common axis of rotation 15. A rotary shaft 13 is formed with an outer unbalanced mass 14 as a hollow shaft. A free end of the other rotary shaft 13 with an inner unbalanced mass 14 is mounted within the hollow shaft. The rotary shafts 13 are mounted in a housing 11 via additional roller bearings 16 and are driven by their own drives 19 . The centrifugal forces of the rotating unbalanced masses 14 act in a common plane, so that no potentially disruptive tilting moments occur. This storage variant is particularly suitable for a vibration exciter 12 with only two unbalanced masses 14.

In the Figures 7 to 9 the effect of a variable second phase shift Δφ ₂ is explained using two unbalanced masses 14 rotating in the same direction. The positions of the unbalanced masses 14 relative to one another are shown on the left. The axes of rotation 15 are in the longitudinal direction of the track 8 aligned and thus run parallel to a z-axis of an in 1 drawn right-hand Cartesian coordinate system x, y, z. Diagrams show directional components F _x , F _y of a resulting impact force Fs over a common phase angle ϕ. Below that, impact force vectors are shown for several phase angles φ in the coordinate system x, y, z moved along with the machine 1 . When in a starting position according to 7 the second unbalanced mass 14 is phase-shifted by 180° with respect to the first unbalanced mass 14, the centrifugal forces are eliminated. The resulting directional components F _y , F _x of the impact force Fs are equal to zero.

Opposite the starting position is in 8 a second phase shift Δφ ₂ of 60° is set for the second unbalanced mass 14 in the direction of rotation, so that the second unbalanced mass 14 leads the first unbalanced mass 14 by a total of 240°. This results in a rotating impact force Fs with a constant amount. The maximum impact force Fs is achieved when a second phase shift Δφ ₂ of 180° in the direction of rotation is set for the second unbalanced mass 14 compared to the starting position. Then both unbalanced masses 14 rotate synchronously, so that the centrifugal forces add up ( 9 ).

Corresponding illustrations are in Figures 10 and 11 shown for two unbalanced masses 14 driven in opposite directions. In a starting position, the impact force component F _y in the y-direction is eliminated and the greatest impact force (Fs) occurs in the x-direction ( 10 ). A change in the impact force Fs occurs when a first phase shift Δφ ₁ is set for an unbalanced mass 14 in relation to the starting position. In 11 the first phase shift Δφ ₁ of the second unbalanced mass 14 is, for example, 60° in the direction of rotation. The impact force Fs is then reduced. The effective direction of the impact force Fs has an angle of inclination relative to the x-axis which corresponds to half the first phase shift Δφ ₁ . A maximum impact force Fs parallel to the y-axis thus results with a first phase shift Δφ ₁ of 180°.

In the Figures 12 to 16 are different phase shifts Δϕ ₁ , Δϕ ₂ for four unbalanced masses A, B, C and D according to Figures 3 and 4 shown. Each of the Figures 12 to 15 shows on the left a first initial position of two pairs of unbalanced masses 34, each with unbalanced masses A, B and C, D rotating in opposite directions (phase angle φ=0). Besides ( 12, 13 ) or below ( 14 , 15 ) courses of the impact forces F _AB , F _CD of the pairs of unbalanced masses 34 and the resulting impact force Fs are shown over a common phase angle φ. Furthermore, the positions of the unbalanced masses 14 are shown at a phase angle φ of 90°, 180° and 270°.

Based on Figures 12 and 13 an impact force adjustment in the direction of the x-axis, ie in the track plane normal to the longitudinal direction 8 of the track, is explained. The unbalanced masses A, B or C, D of each unbalanced mass pair 34 are phase-shifted by 180° with respect to one another. As a result of the opposite directions of rotation 30, the centrifugal forces in the direction of the y-axis are eliminated and the y-component of the impact force Fs is equal to zero. In 12 the unbalanced masses A, C or B, D, which can be driven in the same direction of rotation, are also phase-shifted by 180° with respect to one another. This also results in a canceled x-component for the overall resulting impact force Fs. In this initial position, despite the rotating unbalanced masses 14, no impact force Fs acts on the track 3.

For a maximum impact force Fs in the x-direction, the set second phase shift Δϕ ₂ is equal to 180° ( 7 ). Here, the imbalance masses A, C or B, D that can be driven in the same direction of rotation run synchronously, so that the centrifugal forces add up in the x-direction. With the variably adjustable second phase shift Δϕ ₂ in the range from 0° to 180°, the resulting impact force Fs in the direction of the x-axis can be precisely adjusted from zero to a maximum.

The setting of the impact force Fs in the direction of the y-axis is based on the figures 14 and 15 explained. First, in each pair of unbalanced masses 34, an unbalanced mass B or D is in relative to the starting position 12 out of phase. Specifically, a first phase shift Δφ ₁ equal to 180° is set for both pairs of unbalanced masses 34, so that a there is complete cancellation of the resulting impact force Fs ( 14 ). In order to achieve a maximum impact force Fs in the direction of the y-axis, a second phase shift Δϕ ₂ equal to 180° is set compared to this new starting position ( 15 ).

16 shows five different impact force settings with the resulting impact force Fs for four unbalanced masses A, B, C, D. Four positions of the respective impact force setting are shown from left to right, namely with the phase angle ϕ equal to 0°, 90°, 180° and 270° . The required impact force Fs is set quickly and precisely by changing the specification of the first phase shift Δφ ₁ and the second phase shift Δφ ₂ by means of the common control device 31 . In this case, the control device 31 includes a computing unit in order to set the optimum impact force Fs as a function of a local track condition. Corresponding sensor signals from sensors arranged on the machine 1 or previously determined track data are fed to the control device 31 for this optimization process.

Claims (10)

1. A machine (1) for stabilizing a track (3), including a machine frame (6) supported on on-track undercarriages (4) and a vertically adjustable stabilizing unit (7) designed to roll on rails (5) of the track (3) by means of unit rollers (10), the stabilizing unit comprising a vibration exciter (12) with rotating imbalance masses (14) for generating an impact force (Fs) acting dynamically in a track plane perpendicularly to a track longitudinal direction (8) and a vertical drive (9) for generating a vertical load acting on the track (3), characterized in that the vibration exciter (12) comprises at least four rotatable imbalance masses (14) of which two imbalance masses (14) in each case are driveable right-turning and two imbalance masses (14) are driveable left-turning, that the right-turning imbalance masses (14) and the left-turning imbalance masses (14) each forming an imbalance mass pair (34) are driveable applying a first phase shift (Δϕ₁) which is variably adjustable with respect to an initial position, that the two left-turning imbalance masses (14) are driveable with a variably adjustable second phase shift (Δϕ₂) to one another, and that the two right-turning imbalance masses (14) are driveable with a variably adjustable second phase shift (Δϕ₂) to one another.
2. A machine (1) according to on claim 1, characterized in that an angle sensor (35) is associated with each imbalance mass (14).
3. A machine (1) according to claim 1 or 3, characterized in that the respective imbalance mass (14) is arranged on the stabilizing unit (7) with a rotation axis (15) being aligned in the track longitudinal direction (8).
4. A machine (1) according to one of claims 1 to 3, characterized in that a separate drive (19) is associated with each imbalance mass (14).
5. A machine (1) according to one of claims 1 to 3, characterized in that a common drive (19) is associated with two imbalance masses (14).
6. A machine (1) according to one of claims 4 or 5, characterized in that the respective drive (19) is designed as an electric drive.
7. A machine (1) according to claim 6, characterized in that the electric drives are controlled by means of a common control device (31).
8. A machine (1) according to one of claims 4 or 5, characterized in that the respective drive (19) is designed as a hydraulic drive.
9. A machine (1) according to one of claims 4 to 8, characterized in that an adjustment device (25) for a variable phase shift (Δϕ₁, Δϕ₂) is associated with the respective drive (19).
10. A method of operating a machine (1) according to one of claims 1 to 9, characterized in that the stabilizing unit (7) is set down on the track (3) via the vertical drive (9) and actuated with a vertical load, and that at least four rotatable imbalance masses (14) are driven applying variably adjustable phase shifts (Δϕ₁, Δϕ₂) to one another in this way, that two right-turning imbalance masses (14) and two left-turning imbalance masses (14) each forming an imbalance mass pair (34) are driven applying a first phase shift (Δϕ₁) which is variably adjustable with respect to an initial position and that the two left-turning imbalance masses (14) are driven applying a variably adjustable second phase shift (Δϕ₂) to one another and the two right-turning imbalance masses (14) are driven applying a variably adjustable second phase shift (Δϕ₂) to one another.

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