MÁQUINA COM UMA UNIDADE DE SOCARIA E MÉTODO PARA OPERAR UMA MÁQUINA
Patent Information
- Authority / Receiving Office
- BR · BR
- Patent Type
- Patents
- Current Assignee / Owner
- PLASSER & THEURER EXPORT VON BAHNBAUMASCHINEN GMBH
- Filing Date
- 2021-06-02
- Publication Date
- 2026-08-04
Smart Images
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Abstract
Description
1 / 16 MACHINE WITH A TAMPING UNIT AND METHOD FOR OPERATING A MACHINE Technology Field
[001] The invention relates to a machine with a tamping unit for the simultaneous tamping of a plurality of railway sleepers, positioned immediately one behind the other, by means of a plurality of tamping units arranged immediately one behind the other in relation to a longitudinal direction of the machine, wherein each tamping unit comprises a height-adjustable tamping tool holder on which opposing tamping tools are mounted, the tamping tools being coupled to a vibration unit arranged in the tamping tool holder by means of clamping cylinders. The invention further relates to a method for operating the machine. Previous Technique
[002] In order to restore or maintain a predefined railway track geometry, ballasted tracks are regularly worked using tamping machines. In the process, the tamping machine moves along the railway track and raises the railway track panel formed of sleepers and rails to a target level by means of a lifting and marking unit. The new railway track position is fixed by tamping the ballast using a tamping unit. The tamping unit comprises tamping tools with tamping teeth which, during tamping, penetrate the ballast bed while being subjected to vibration and being squeezed towards each other. In the process, the ballast is compacted below the respective sleeper.
[003] Tamping units for the simultaneous tamping of a plurality of sleepers are used particularly in flat track tamping machines. Given the resulting high working speed, the railway track can be maintained on short railway holdings. Modern tamping machines Petition 870260003169, dated 13 / 01 / 2026, page 13 / 37 2 / 16 are also characterized by low wear effects on both the tamping unit and the ballast.
[004] A generic machine with at least two tamping unit segments arranged one behind the other is known from EM 513 034 A1. Each tamping unit segment is arranged with adjustable height on a shared tamping unit support. A tamping cycle begins with the tamping unit segments being lowered simultaneously. The simultaneous lowering of adjacent tamping unit segments for tamping adjacent sleepers in the longitudinal direction of the machine happens with a time delay. This facilitates in particular the insertion of immediately adjacent tamping teeth penetrating a shared sleeper cradle. Presentation of the Invention
[005] The object of the invention is to improve a machine of the type mentioned above in such a way that, in addition to a reduced wear effect, a low noise emission is achieved. Additionally, a corresponding method for operating the improved machine is to be indicated.
[006] According to the invention, these objectives are achieved through the features of independent claims 1 and 12. Dependent claims indicate advantageous embodiments of the invention.
[007] The respective vibration unit comprises an eccentric shaft with a first eccentric disc and a second eccentric disc, whose geometric axes of symmetry, together with a common geometric axis of rotation, extend in two eccentric planes that enclose an angle with respect to each other, wherein a first clamping cylinder is mounted on the first eccentric disc, wherein a second opposing clamping cylinder is mounted on the second eccentric disc, and wherein the geometric axes of the opposing clamping cylinders Petition 870260003169, dated 13 / 01 / 2026, page 14 / 37 3 / 16 enclose a position angle that is close to the relative angle of the eccentric planes. In this mode, the angular positions of the eccentric discs and clamping cylinders are harmonized with each other in order to achieve a mass balance for the vibrating parts of the tamping unit. In particular, the inertial forces of the synchronously vibrating tamping tools cancel each other out. As a result, the tamping unit operates more quietly.
[008] The clamping cylinders are not horizontally aligned, meaning that the relative angle is not equal to 180°. In the case of obliquely connected clamping cylinders, the arrangement according to the invention causes ideal vibration of the tamping tools that move synchronously towards each other in opposite directions. Specifically, the vibrations of the two opposing tamping tools undergo a phase change that causes their respective inversion points to be reached simultaneously. The acceleration and deceleration forces of the vibrating masses of the tamping tools and the vibrating partial masses of the clamping cylinders cancel each other out.
[009] Tamping teeth arranged at the lower free ends of the tamping tools vibrate synchronously towards each other in opposite directions with maximum relative movement. This results in maximum energy input into the ballast bed without setting up the tamping tool holder and associated tamping unit suspension for disturbance reaction vibrations. The tamping unit and the machine thus have low vibration stress. Both the components of the tamping unit and the ballast grains of the ballast bed to be compacted are consequently protected. Together, the targeted introduction of vibrations into the ballast bed and the mass balance result in a reduction in noise emission compared to designs Petition 870260003169, dated 13 / 01 / 2026, page 15 / 37 4 / 16 known units of tamping.
[010] Advantageously, each tamping unit segment comprises at least one clamping cylinder, whose geometric axis of the cylinder is oriented obliquely downwards, in particular with an angle of inclination greater than 20° with respect to a horizontal line. In this way, a particularly narrow design of the individual tamping unit segments in the longitudinal direction of the machine is possible, so that even railway tracks with small sleeper spacing can have the sleepers worked simultaneously with all tamping unit segments.
[011] In a further advantageous development, the respective eccentric shaft is connected to a flywheel. During operation, the eccentric shaft is driven together with the flywheel at a predefined rotational speed. The flywheel has a stabilizing effect on the rotational speed. Specifically, the backspin moments of the tamping tools and vibratory clamping cylinders are balanced with the kinetic energy temporarily stored in the flywheel during a vibration cycle. The vibration amplitude of the tamping tools is maintained independently of the stiffness of the ballast bed.
[012] For further improvement of mass balance, the rotating unit formed of the eccentric shaft and flywheel is designed in such a way that a common center of mass with respect to the geometric axis of rotation is opposite to the geometric axes of symmetry of the two eccentric discs. In this way, the rotating unit acts as a balancing mass for the moving mass of the clamping cylinders of the opposing tamping tools.
[013] In an advantageous embodiment of the invention, the tamping unit comprises – with respect to the longitudinal direction of the machine – front tamping unit segments and Petition 870260003169, dated 13 / 01 / 2026, page 16 / 37 5 / 16 rear segments with asymmetrically arranged clamping cylinders and central tamping unit segments with symmetrically arranged clamping cylinders. The central tamping unit segments have a particularly narrow design such that sleepers with small sleeper spacings can also be tamped at the same time. On one half facing the central tamping unit segments, the front and rear tamping unit segments also have a narrow design. The halves of the front and rear tamping unit segments facing away from the central tamping unit segments have a wider design to achieve a greater opening width between the opposing tamping tools.
[014] In this embodiment of the invention, it is useful if each of the front and rear tamping unit segments has an eccentric shaft with different eccentricities. Different lever ratios of the opposing tamping tools and the different eccentricities are harmonized with each other in such a way that the vibration amplitudes of the freely vibrating tamping tooth tips are of equal size.
[015] The respective opposing tamping tools of the front and rear tamping unit segments are advantageously mounted on the associated tamping tool holder with vertically spaced articulation joints. Preferably, the joints of the tamping tools facing the central tamping unit segments are arranged lower in order to achieve a narrower design while maintaining the same leverage ratio.
[016] Furthermore, it is useful if each of the front and rear tamping unit segments has one half facing the central tamping unit segments, which is constructed according to a half-symmetry of the segments. Petition 870260003169, dated 13 / 01 / 2026, page 17 / 37 6 / 16 central tamping unit. This simplifies the tamping unit structure and facilitates the operation of individual tamping unit segments. Furthermore, the number of individual spare parts is reduced.
[017] Advantageously, each of the central tamping unit segments and the halves of the front and rear tamping unit segments facing the central tamping unit segment is connected to a first clamping pressure system, and each of the halves of the front and rear tamping unit segments facing away from the central tamping unit segments is connected to a second clamping pressure system. The different clamping pressure systems enable the presence of the same static and dynamic clamping forces in all tamping tools.
[018] A further improvement allows one half of the respective front or rear tamping unit segment facing away from the central tamping unit segments to comprise a clamping cylinder with an increased stroke in order to tam double sleepers. In this mode, the tamping unit can be used universally and all sleeper arrangements occurring on a railway line can be worked.
[019] Furthermore, it is advantageous if several tamping tools arranged close to each other transversely to the longitudinal direction of the machine, together with the associated clamping cylinder, form a jointly actuatable clamping group. This applies to tamping unit segments that are arranged close to each other, tamping a sleeper on either side of both rails of the railway track. During operation, the clamping groups are actuated together in order to ensure a uniform compaction process along a sleeper. Petition 870260003169, dated 13 / 01 / 2026, page 18 / 37 7 / 16
[020] In the method according to the invention for operating the described machine, the vibration unit and the clamping cylinders of the respective tamping unit segment are actuated in such a way that the position angle of the clamping drives oscillates within a range around the relative angle of the eccentric planes of the associated eccentric shaft. In this mode, the current position angle remains close to the relative angle during a tamping process. Particularly in an intermediate articulation position of the clamping drives, the position angle corresponds to the relative angle. The vibrating masses of the respective tamping unit segment then vibrate synchronously in opposite directions, resulting in a mass balance. This minimizes stress on the tamping unit as well as noise development.
[021] A further development of the method allows each eccentric shaft to be driven by means of an associated vibration drive motor and all vibration drive motors to be driven by means of a shared control device for synchronous operation. The vibration movements of the tamping drive segments are thus harmonised with each other in order to optimize the smooth operation of the total tamping drive unit.
[022] Furthermore, it is advantageous if the respective eccentric shaft is driven at a variable rotational speed depending on the height position of the associated tamping unit segment. Before a tamping process, all tamping unit segments are in an initial position above the railway track. In this position, the rotational speed of the respective eccentric shaft remains reduced to further reduce noise development. Only when the height position is changed during a lowering process is there an increase to a higher speed. Petition 870260003169, dated 13 / 01 / 2026, page 19 / 37 8 / 16 rotational work speed, which is greater during a penetration process than during tightening.
[023] A further improvement allows clamping groups arranged close to each other transversely to the longitudinal direction of the machine to be activated with a shared control signal. In this mode, a uniform compaction process takes place along a sleeper.
[024] Advantageously, during a tightening process, each of the central tamping unit segments and the halves of the front and rear tamping unit segments facing the central tamping unit segments is subjected to a first tightening pressure, while each of the halves of the front and rear tamping unit segments facing away from the central tamping unit segments is subjected to a second tightening pressure. The different tightening pressures enable the presence of the same static and dynamic tightening forces in all tamping tools. Brief Description of the Drawings
[025] In the following content, the invention is explained by way of example with reference to the accompanying figures. The following figures show schematic illustrations: Figure 1 Machine with tamping unit Figure 2: Tamping unit for simultaneous tamping of three sleepers in side view. Figure 3. Side view of a central tamping unit segment. Figure 4 Kinematics according to Figure 3 Figure 5 Kinematics according to Figure 3 in various working positions Figure 6. Front and rear tamping unit segment in side view. Figure 7 Kinematics according to Figure 6 Petition 870260003169, dated 13 / 01 / 2026, page 20 / 37 9 / 16 Figure 8 Kinematics according to Figure 6 in various working positions Figure 9 Eccentric shaft in side view Figure 10 Eccentric shaft in top view Figure 11 Tamping unit in front view Figure 12 Tamping unit for simultaneous tamping of four sleepers Description of the Modalities
[026] The machine 1 shown in Figure 1 is designed as a flat track tamping machine for simultaneous tamping of three sleepers 4 supported on a ballast bed 2 of a railway track 3. The machine 1 comprises a machine frame 6 supported by rail-based displacement mechanisms 5, on which a tamping unit 7 is mounted. In addition, the machine 1 comprises a lifting and marking unit 8 for lifting and marking the railway track panel formed of sleepers 4 and rails 9. A current railway track position is recorded by means of a measuring system 10.
[027] The tamping unit 7 is fixed to the machine frame 6 by means of an adjustment device 11. It comprises a tamping unit frame 12 with guide rods 13 and a plurality of tamping unit segments 14. In a variant not shown, each tamping unit segment 14 is designated with a separate tamping unit frame 12. Each tamping unit segment 14 comprises a tamping tool holder 15 which is mounted on the associated guide rods 13 with a height adjustable by means of a height adjustment unit 16. The opposing tamping tools 18 are tiltably mounted on the respective tamping tool holder 15 in a longitudinal direction 17 of the machine.
[028] In addition, a vibration unit 19 is arranged in the respective tamping tool holder 15 to which the Petition 870260003169, dated 13 / 01 / 2026, page 21 / 37 10 / 16 tamping tools 18 are coupled by means of clamping cylinders 20. Each tamping tool 18 comprises a pivot lever 21 with an upper lever arm and a lower lever arm. The pivot lever 21 is mounted on the associated tamping tool holder 15 by means of a pivot joint 22, with the upper lever arm being connected to the associated clamping cylinder 20. Two tamping teeth 23 are usually fixed to the free lower lever arm.
[029] In an initial position (Figure 2), the opposing tamping teeth 23 of the respective tamping unit segment 14 have the same spacing with respect to a central vertical plane 24. The spacing between the central vertical planes 24 of the tamping unit segments 14 arranged one behind the other corresponds to the smallest sleeper spacing t of the sleepers 4 to be tamped. The dimensioning of the tamping unit segments 14 in the longitudinal direction 17 of the machine is thus based on this smallest sleeper spacing t.
[030] A central tamping unit segment 14 arranged between a front and a rear tamping unit segment 14 has a narrow design in the longitudinal direction 17 of the machine. This requirement is achieved by means of clamping cylinders 20 oriented obliquely downwards. In the case of the front and rear tamping unit segments 14, only the half facing the central tamping unit segment 14 is designed accordingly. The other half has a clamping cylinder 20 oriented approximately horizontally. In this mode, a greater articulation range of the associated tamping tool 18 is obtained. The increase in the opening width between the opposing tamping teeth 23 that can be achieved in this mode enables adjustment for larger sleeper spacings t or for double sleepers a Petition 870260003169, dated 13 / 01 / 2026, page 22 / 37 11 / 16 to be punched.
[031] The structure of the central tamping unit segment 14 is explained in more detail with reference to Figures 3 to 5. Figure 4 shows a kinematic model of the tamping unit segment 14 shown in Figure 3. Figure 5 shows the kinematic model 3 in three working positions. On the tamping tool holder 15, an eccentric shaft 25 of the vibration unit 19 is mounted. During operation, the eccentric shaft 25 rotates around a geometric axis of rotation 26. The eccentric shaft 25 comprises two eccentric discs 27, 28 offset from each other, whose geometric axes of symmetry 29, 30 have a respective eccentricity e1, e2 with respect to the geometric axis of rotation 26.
[032] Furthermore, the geometric axes of symmetry 29, 30 and the geometric axis of rotation 26 extend into two eccentric planes 31, 32, which enclose an angle δ with respect to each other. The geometric axes of cylinders 33 of the clamping cylinders 20 include a position angle β. In the case of the central tamping unit segment 14, the opposing clamping cylinders 20 are arranged symmetrically. The respective geometric axis of cylinder 33 is obliquely inclined downwards at an angle of inclination α with respect to a horizontal line. The angle of inclination α is at least 20°. Ideally, the angle of inclination α is defined in a range between 30° and 50° to ensure optimal power transmission beyond the narrow design.
[033] The tilt angle α and the position angle β change slightly during a tamping process as a result of vibration and clamping movements. For better illustration, Figure 5 shows the various positions of the clamping cylinders 20 when the eccentric shaft 25 is stationary. The solid lines show a clamped position of the tamping tools 18. In the position shown, the shafts Petition 870260003169, dated 13 / 01 / 2026, page 23 / 37 12 / 16 geometric cylinder axes 33 are situated in eccentric planes 31, 32, such that the position angle β is equal to the relative angle δ. Also for better illustration, the eccentricities e1, e2 are shown disproportionately large compared to the other dimensions. The circular motion of the clamping cylinder joints 20 resulting during a rotation of the eccentric shaft 25 is not taken into account in the illustration. Its influence on the changes in the position of the geometric cylinder axes 33 is negligible compared to the influence of the clamping movements caused by a piston displacement.
[034] As soon as the eccentric shaft 25 starts rotating during operation, the eccentric planes 31, 32 will also rotate with an unchanged relative angle δ. The position angle β varies within a range of emin-emax, which depends on the kinematic design of the tamping unit segment 14 and the piston stroke. During a tamping process, the tamping cylinders 20 rotate slightly around the geometric axes of symmetry 29, 30 of the eccentric discs 27, 28. In Figure 5, the two extreme positions are shown with dashed and dashed-dotted lines respectively. The value of the position angle β always remains close to the value of the relative angle δ. With the optimized kinematic design of the tamping unit segment 14, the value of the relative angle δ is always within the emin-emax range of values of the position angle β during operation.
[035] For the front and rear tamping unit segments 14, corresponding kinematic relationships are shown in Figures 6 to 8. In contrast to the central tamping unit segment 14, the clamping cylinders 20 and tamping tools 18 are arranged asymmetrically here. The articulation levers 21 designated for the different clamping cylinders 20 are adjusted accordingly. On the side facing the unit segment of Petition 870260003169, dated 13 / 01 / 2026, page 24 / 37 13 / 16 central tamping 14, the geometric axis of cylinder 33 of the clamping cylinder 20 is oriented obliquely downwards in relation to a horizontal line with the angle of inclination α.
[036] Figure 8 shows that the intermediate positions of the two clamping cylinders 20 do not occur simultaneously with respect to their respective articulation range. In the clamped position shown (solid lines), the smaller clamping cylinder 20 is in the intermediate position and the larger clamping cylinder 20 is in a final position tilting downwards. In this position, the minimum position angle emin occurs. During a return movement of the tamping tools 18, the larger clamping cylinder 20 passes through its intermediate position, in which the position angle β corresponds to the value of the relative angle δ of the eccentric shaft 25. After the return movement, the position angle β has the largest value emax. Thus, during a clamping and return movement, the value of the position angle β oscillates in the emin-emax range around the value of the relative angle δ of the eccentric planes 31, 32.
[037] In order to ensure approximately equal leverage transmission on both sides, the articulation joints 22 are spaced vertically in the tamping tool holder 15. The larger design of the nearly horizontally oriented clamping cylinder 20 allows for a greater clamping distance. As a result, the position angle β oscillates over a larger range of min-max values.
[038] Figures 9 and 10 show the eccentric shaft 25 for the front or rear tamping unit segment 14 in detail. For the sectional view in Figure 10, the cut is shown in Figure 9. The first eccentric disc 27 is centered along the eccentric shaft 25. On this first eccentric disc 27, the smaller clamping cylinder 20, oriented obliquely downwards, is mounted. The second eccentric disc 28 is divided into two parts, by which the discs Petition 870260003169, dated 13 / 01 / 2026, page 25 / 37 14 / 16 partial eccentrics are arranged on either side of the first eccentric disc 27. The larger clamping cylinder 20 is mounted with a fork-shaped end on top of them. Both clamping cylinders 20 are shown in Figures 9, 10 with dashed and dotted lines.
[039] In the position shown, the geometric axes of the clamping cylinders 20 are within the range of the eccentric planes 31, 32. In this, the vibrations of both clamping cylinders 20 reach an external inversion point at the same time. As the eccentric shaft 25 continues to rotate, the ends of the clamping cylinders 20 mounted on the eccentric discs 27, 28 are displaced in opposite directions. Because of the synchronous vibrations, the vibrating masses balance each other to a great extent. This applies in particular to the synchronously vibrating tamping teeth 23.
[040] The mass balance is reinforced with a flywheel 34, which rotates with the eccentric shaft 25 around the same geometric axis of rotation 26. The eccentric shaft and the flywheel 34 form a rotating unit whose center of mass 35 lies approximately in a plane of symmetry 36 of both eccentric planes 31, 32. Here, the center of mass 35 is spaced from the geometric axis of rotation 26 and lies opposite the geometric axes of symmetry 29, 30 of both eccentric discs 27, 28. The flywheel 34 with the off-center center of mass 35 acts against the inertial forces of the vibrating clamping cylinders 20. The dimensions of the flywheel 34 correspond with the mass of the clamping cylinder 20. The flywheel 34, for example, is designed as a disc which, in order to achieve the off-center center of mass 35, has a flattened area or a groove.
[041] On the eccentric shaft 25 shown for the front or rear tamping drive segment 14, the eccentricities e1, e2 having different sizes cause Petition 870260003169, dated 13 / 01 / 2026, p. 26 / 37 15 / 16 equal amplitudes at the free ends of the tamping teeth 23. Because of the symmetrical arrangement, both eccentricities e1, e2 on the eccentric axis 25 for the central tamping unit segment 14 are of equal size.
[042] Figure 11 shows that two separately lowerable tamping unit segments 14 are assigned to each rail 9 of the railway track 3. Thus, the tamping unit 7 comprises four tamping unit segments 14 arranged close to each other in a bank arrangement. For each tamping unit segment 14, the associated eccentric shaft 25 is driven by a vibration unit motor 37. All vibration unit motors 37 are driven by means of a shared control device 38 to ensure synchronous operation. In this mode, the vibrations of the individual tamping unit segments 14 cancel each other out, minimizing vibrations transmitted from the tamping unit 7 to the machine structure 6.
[043] In a simplified variant not shown, a combined tamping unit segment 14 with tamping tools 18 on the inside of the rail and tamping tools 18 on the outside of the rail is assigned to each rail 9. In this case, the tamping unit 7 comprises two combined tamping unit segments 14 arranged close to each other in a bank arrangement.
[044] To tamp a sleeper 4, the tamping unit segments 14 arranged close to each other form clamping groups, whose tamping teeth 23 are lowered together and tightened together (two clamping groups per bank). A tamping unit 7 with four banks of tamping unit segments 14 arranged one behind the other is shown in Figure 12. This results in eight clamping groups, each of which is actuated together. The clamping groups of the central tamping unit segments 14 and the Petition 870260003169, dated 13 / 01 / 2026, page 27 / 37 16 / 16 clamping groups of the front and rear tamping unit segments 14 facing them are supplied by means of a first clamping pressure system 39. The frontmost clamping group and the rearmost clamping group are supplied by means of a second clamping pressure system 40.
[045] In this way, differently sized clamping groups are loaded with different clamping pressures during a clamping process. The clamping pressures are harmonized with each other in such a way that the same static and dynamic clamping forces are present on all tamping teeth 23. To ensure a uniform clamping process along a sleeper 4, the respective clamping group is activated with a shared control signal. Petition 870260003169, dated 13 / 01 / 2026, pp. 28 / 37
Claims
1 / 4 CLAIMS 1. Machine (1) with a tamping unit (7) having a plurality of tamping unit segments (14) arranged one behind the other in relation to a longitudinal direction of the machine (17) for the simultaneous tamping of a plurality of railway sleepers (4) (3), positioned immediately one behind the other, wherein each tamping unit segment (14) comprises a height-adjustable tamping tool holder (15) on which opposing tamping tools (18) are mounted, which are coupled to a vibration unit (19) arranged in the tamping tool holder (15) by means of clamping cylinders (20), characterized in that the respective vibration unit (19) comprises an eccentric shaft (25) with a first eccentric disc (27) and a second eccentric disc (28), whose geometric axes of symmetry (29, 30), together with a common geometric axis of rotation (26), extend into two eccentric planes (31,32) that enclose a relative angle (δ) with respect to each other, that a first of the clamping cylinders (20) is mounted on the first eccentric disc (27), a second of the opposite clamping cylinders (20) is mounted on the second eccentric disc (28), and that the geometric cylinder axes (33) of the first clamping cylinder (20) and the geometric cylinder axes (33) of the opposite second clamping cylinder (20) enclose a position angle (β) that is close to the relative angle (δ) of the eccentric planes (31, 32).
2. Machine (1), according to claim 1, characterized in that each segment of the tamping unit (14) comprises at least one clamping cylinder (20), whose geometric axis of the cylinder (33) is oriented obliquely downwards, in particular with an angle of inclination (α) greater than 20° with respect to a horizontal line. Petition 870260003169, dated 13 / 01 / 2026, page 29 / 37 2 / 4 3. Machine (1), according to claim 1 or 2, characterized in that the respective eccentric shaft (25) is connected to a flywheel (34).
4. Machine (1), according to claim 3, characterized in that the eccentric shaft (25) and the flywheel (34) form a rotating unit with a center of mass (35) that lies opposite the geometric axes of symmetry (29, 30) of both eccentric discs (27, 28) with respect to the geometric axis of rotation (26).
5. Machine (1), according to any one of claims 1 to 4, characterized in that the tamping unit (7) comprises front and rear tamping unit segments (14) with asymmetrically arranged clamping cylinders (20) and central tamping unit segments (14) with symmetrically arranged clamping cylinders (20).
6. Machine (1), according to claim 5, characterized in that each of the front and rear tamping unit segments (14) has an eccentric shaft (25) with different eccentricities (e1, e2).
7. Machine (1), according to claim 5 or 6, characterized in that each of the front and rear tamping unit segments (14) has opposing tamping tools (18) that are mounted on the tamping tool holder (15) associated with vertically spaced articulation joints (22).
8. Machine (1), according to any one of claims 5 to 7, characterized in that each of the front and rear tamping unit segments (14) has a half facing the central tamping unit segments (14), which is constructed according to a half-symmetry of the central tamping unit segments (14). Petition 870260003169, dated 13 / 01 / 2026, pp. 30 / 37 3 / 4 9. Machine (1), according to claim 8, characterized in that each of the central tamping unit segments (14) and the halves of the front and rear tamping unit segments (14) facing the central tamping unit segments (14) is connected to a first clamping pressure system (39), and that each of the halves of the front and rear tamping unit segments (14) facing away from the central tamping unit segments (14) is connected to a second clamping pressure system (40).
10. Machine (1), according to claim 8 or 9, characterized in that one half of the respective front or rear tamping unit segment (14) facing away from the central tamping unit segments (14) comprises a clamping cylinder (20) with an increased stroke in order to tam double sleepers.
11. Machine (1), according to any one of claims 1 to 10, characterized in that several tamping tools (18) arranged close to each other transversely to the longitudinal direction of the machine (17), together with the associated clamping cylinder (20), form a jointly actuatable clamping group.
12. Method for operating a machine (1) as defined in any one of claims 1 to 11, characterized in that the vibration unit (19) and the clamping cylinders (20) of the respective tamping unit segment (14) are actuated in such a way that the position angle (β) of the clamping drives (20) oscillates within a range around the relative angle (δ) of the eccentric planes (31, 32) of the associated eccentric shaft (25).
13. Method according to claim 12, characterized in that each eccentric shaft (25) is driven by means of an associated vibration drive motor (37), and all vibration drive motors (37) are driven by means of a shared control device (38) for synchronous operation.
14. Method, according to claim 12 or 13, characterized in that clamping groups arranged close to each other transversely to the longitudinal direction of the machine (17) are actuated with a shared control signal.
15. Method, according to any one of claims 12 to 14, characterized in that each of the central tamping unit segments (14) and the halves of the front and rear tamping unit segments (14) facing the central tamping unit segments (14) is loaded with a first tightening pressure, and each of the halves of the front and rear tamping unit segments (14) facing away from the central tamping unit segments (14) is loaded with a second tightening pressure during a tightening process. Petition 870260003169, dated 13 / 01 / 2026, pp. 32 / 37