EP2504490B1 - Compaction device and method for compacting ground - Google Patents

Description

The invention relates to a compacting device for compacting trays according to the preamble of claim 1, as well as to a method for compaction of trays according to claim 16.

Compactors are known, e.g. in the form of a road roller.

With the aid of a road roller, floors, e.g. Asphalt ceilings are compacted. Sufficient compaction is necessary to be able to ensure the load capacity and durability of the soil. The road rollers distinguish between a dynamic and a static mode of compression. In the dynamic mode of operation, the compaction takes place by movement, and in the static mode of operation, the compaction is carried out by the weight of the road roller.

A road roller may be a self-propelled vehicle and has at least one bandage.

When driving through curves with a bandage of a compactor in the form of a road roller there is an inner and outer radius of curvature of the bandage at their lateral ends. At the outside edge of the bandage, the speed is higher due to the longer distance traveled, as at the inner edge. Increasing the steering angle and thus reducing the radius of the curve increases the difference between these speeds. However, since a bandage can not rotate at different circumferential speeds at its lateral ends, the bandage rolls in the middle of its width on the ground from while at the outer edge regions of the bandage to thrust movements (slippage) between the asphalt and the rolling mantle Bandage is coming. For this reason, it makes sense to divide the bandage and drive both halves independently, thus reducing this inevitable effect due to the reduced width of the split bandage.

Oszillationsbandagen are so far, in contrast to vibration bandages not made in split design, since the technical realization is much more difficult. The synchronization of the centrifugal forces generating imbalances must be guaranteed at all times, especially with a relative rotation of the two bandages each other.

In a known oscillating roller after WO 82/01903 Two synchronously rotating imbalance shafts are provided, which are driven via a central shaft by means of a toothed belt. This imposes a fast changing forward / backward rotating motion on the roller. The oscillating roller never lifts off from the surface.

Of the WO 82/01903 ( Fig. 5 ), four typical operating states of the prior art undivided oscillation band oscillation system can be seen. From left to right, the positions of the imbalances are each further rotated in steps of 90 ° (out of phase).

im (Fig. 5B) bzw. gegen den Uhrzeigersinn (Fig. 5D).Due to the coupled drive, both imbalances (imbalance weights) rotate in the same direction. While in the operating states of the left illustrations of the Figure 5 the centrifugal forces cancel, resulting in the illustrations on the right side ( Fig. 5B, 5D ) due to the directions of the centrifugal forces F and the lever arms x a torque $$\mathrm{M}=\mathrm{2}•\mathrm{x}•\mathrm{F}$$

in the ( Fig. 5B ) or counterclockwise ( Fig. 5D ).

The bandage thus undergoes a small twist to the left and right with each revolution of the imbalance shaft and begins to oscillate about the axis of rotation M of the bandage.

In vibration bandages, the division of the bandage is already known, because this is technically easy to implement. Fig.2 In the present description, the sectional view of a split vibration bandage. The two bandage parts 2a, 2b are screwed together via a rotary joint. The imbalances 3 for both bandage parts 2a, 2b are located here on the central imbalance shaft 31, which is driven by a hydraulic motor 7. When cornering and thus rotation of the bandage parts 2a, 2b to each other, nothing changes at the vibration in the two bandage parts 2a, 2b, ie both bandage parts 2a, 2b vibrate synchronously.

• Beim Verdrehen der Bandagenteile 2a, 2b (Walzmäntel) zueinander, z.B. bei Kurvenfahrt, ändert sich die Position der Unwuchtwellen 31a, 31b zueinander, da die Unwuchtwellen 31a, 31b in den jeweiligen Bandagenteilen 2a, 2b gelagert sind. Da die Unwuchten 3, die mittels Zahnriemen 32 von einer zentralen Welle 33 angetrieben werden, ihre Ausrichtung beibehalten, verschiebt sich jeweils die Wirkrichtung der Kraft im verdrehten Bandagenteil 2a, 2b (Fig.4 bis Fig.7).

A simple structure with a continuous central shaft 33 for driving the imbalances 3 as in the vibration bandage, is in an oscillation bandage in Fig. 3 shown. This solution can not solve the phase problem for the following reasons:

• When the bandage parts 2a, 2b (rolling jackets) are rotated relative to one another, eg during cornering, the position of the imbalance shafts 31a, 31b changes with respect to one another, since the imbalance shafts 31a, 31b are mounted in the respective banding part 2a, 2b are. Since the imbalances 3, which are driven by means of toothed belt 32 by a central shaft 33, maintain their orientation, the direction of action of the force in the twisted bandage part 2a, 2b (FIG. Fig.4 to Fig.7 ).

For a better representation of the timing belt guide from the Fig.4 to Fig.7 is the described timing belt guide in Fig. 3 spatially represented.

Fig.4 and Fig.5 show the two bandage parts 2a, 2b before their rotation. In Fig.6 and Fig.7 are the bandage parts 2a, 2b shown by a rotation of the bandage part 2b by 90 °.

For explanation, let it be assumed that the bandage part 2a does not change the position while the bandage part 2b is further rotated by cornering by 90 °. Also, the central rotating shaft is subjected to a snapshot to illustrate and is therefore virtually silent. As Figure 7 shows, the two imbalances of the right bandage part 2b are now one above the other. Since the drive shaft 33 is stationary in the middle of the roll, during the rotation of the bandage part 2b, the toothed belt 32 on the central drive pulley 21 has unrolled and the alignment of the imbalances 3 has not changed. Because of the new position of the imbalances 3, however, the centrifugal forces initiate a moment with maximum leverage, which causes the banding part 2b to rotate. At the position in Figure 6 on the other hand, there is no moment, since the effective lever is zero.

The problem described has the consequence that the bandage parts 2a, 2b can not oscillate synchronously. In extreme cases, when the two bandage parts 2a, 2b work exactly opposite, there are thrust movements in the gap between the bandage parts 2a, 2b and in the adjacent area, which bring about a tearing of the asphalt surface. Depending on the rotation of the two bandage parts 2a, 2b to each other, phase errors of 0 to 180 ° are possible. Already phase errors of 10-20 ° would shave the asphalt at the joint between the band parts 2a, 2b.

From the FR 2748500 a split vibration bandage is known in which the vibration exciters of both bandage halves are mechanically coupled to each other such that the oscillation frequency is synchronized.

From the WO 02/44475 A1 is an oscillating bandage is known in which an oscillatory vibration is generated with a pendulum vibrator.

The invention is therefore based on the object of specifying a vibrating device or a method for compacting trays in which, in the case of divided bandages with oscillatory oscillation, no excessive shearing forces act on the asphalt surface on the joint between the band conveyor parts.

To achieve this object are the features of claim 1 or 16 according to the invention.

According to the invention, it is provided that the bandage is divided at least once with the drive shaft and that each bandage part has at least two coupled vibration exciters mounted in the bandage at a distance from the bandage axis, wherein the vibration exciters of one bandage part are coupled to the vibration exciters of another bandage part, that the vibration exciters all hinge parts swing synchronously relative to each other even with a rotation of the bandage parts.

The respective vibration exciter are stored in the respective band parts.

It is preferably provided that the drive shafts for the vibration exciters of the individual bandage parts are mechanically coupled or adjusted in phase by a control.

The control can be done electrically, electronically or hydraulically / pneumatically.

The drive shafts for the vibration exciter of the adjacent bandage parts can be mechanically coupled via a transmission, wherein the transmission

Rotation or the drive torque of a drive shaft transmits in the correct phase to the subsequent drive shaft.

The transmission for coupling the drive shaft parts may be a planetary gear or a spur gear or a bevel gear.

The bandage is preferably divided into two parts and each bandage part has its own travel drive, wherein the two bandage parts are coaxially rotatable relative to each other rotatably connected to each other.

A preferably usable planetary gear may consist of at least two planetary gear sets.

The planetary gear of two planetary gear sets may have a common planet carrier, wherein the ring gears of the planetary gear sets are each rotatably connected to a bandage part and the respective drive shafts with the respective sun gears of the planetary gear sets.

The gear to drive the imbalances may be a belt transmission or chain transmission.

The transmission for driving the vibration exciters is preferably a toothed belt drive with omega wrap, which drives with unbalanced coupled toothed pulleys.

The transmission is preferably a belt transmission with a belt guide, which allows a reversal of direction and a reciprocal ratio to the planetary gear.

The translation of the belt drive and the translation of the planetary gear should give a total ratio of 1: 1.

It can also be provided a multi-stage planetary gear and a belt drive without reversing direction and without reciprocal ratio to the planetary gear.

The vibration exciters have imbalance weights and the imbalance weights are preferably made of unevenness plates which are preferably laterally attached to the pulleys of the belt transmission and have a radially outwardly extending flank which is aligned in a certain initial position with the belt of the belt drive when the rotational angle offset between the both driven by the belt transmission unbalanced shafts or pulleys corresponds to the target value. Preferably, the belt transmission is a toothed belt transmission.

A belt tensioning device can tension the belt for driving the imbalance or the pulley by means of an eccentrically displaceable bearing pin for the pulley.

The belt tensioner may include an eccentric adjustment bolt for rotating and locking the eccentric journal.

The belt drive can have coaxial and concentric pulleys with the axis of rotation of the imbalances whose weight distribution is not rotationally symmetrical with respect to the axis of rotation of the imbalances.

To the axis of rotation of the imbalances asymmetrically arranged recesses, preferably holes or holes in the material of the toothed belt can cause a non-rotationally symmetric weight distribution and form a negative imbalance mass.

Laterally arranged unbalance plates may be attached to the pulleys and / or asymmetrically arranged screws, which is an imbalance weight form, the screws can also serve to fasten the unbalance plates.

To accommodate the bearings of imbalances flying bearing pins may be provided, the bearings are preferably arranged centrally to the radial belt force and centrifugal force of the imbalances.

These journals are mounted for tensioning the belt displaceable in the blanks of the bandage parts.

For compacting soils with a drum of a compacting device is provided to generate with the aid of at least one vibrator with rotating unbalanced weights compression vibrations of the bandage, by using a split bandage with two bandage halves, wherein the imbalance weights of the vibration exciters in each part of the bandage to the same angle! be rotated with respect to the phase position as the relative rotation of the Bandagenhätften each other to achieve a synchronization of the oscillatory motion in the two halves of the bandage, even if the bandage halves are twisted to each other.

A mechanical connection should enable the synchronization of the exciter forces in both halves of the bandage. This function is performed by a multi-stage planetary gear.

In this case, a transmission has the task to transmit the moment of the hydraulic motor for driving the imbalances from the left to the right bandage in the correct phase.

In the following, embodiments of the invention will be explained in more detail with reference to the drawings.

Show it:

Fig. 1

a vibration device,

Fig. 2

a split vibration bandage of the DV90 roll according to the prior art,

Fig. 3

a simple timing belt guide for split oscillation that can not solve the phase problem

Fig. 4 to 7

different bandage positions,

Fig. 8

a sectional view of the bandage according to the invention,

Fig. 9

a planetary gear set,

Figure 10

a toothed belt drive with omega wrap,

Figure 11

the eccentricity of the unbalance flange / bearing journal, and

Fig. 12

a perspective view of a toothed belt pulley.

Fig. 1 shows as an example of a vibration device, a road roller, namely in particular a tandem vibratory roller with a front and a rear drum 2.

FIGS. 2 to 7 explain, as already mentioned in the introduction, the prior art.

In Figure 8 a split oscillatory bandage 2 is shown. Shown are the two bandage parts 2a, 2b with built-in gear, for example, the in Fig. 9 illustrated planetary gear 6 to solve the phase problem when cornering, imbalances (unbalance weights) 3 of the vibration exciter 30a, 30b and the attachments.

Travel drives 7a, 7b drive the respective bandage parts 2a, 2b. The planetary gear 6 has two planetary gear sets 6a, 6b.

Each bandage part 2a, 2b has an inside arranged frontal Ronde 12a, 12b, in the example, bearing journals 20a, 20b for receiving rotating imbalances 3 of the vibration exciter 30a, 30b are stored.

The ring gear 10a on the left side of the first planetary gear set 6a is fixedly connected to the bandage part 2a on the left side of the bandage 2 by the journal 16a and the round plate 12a. The ring gear 10b on the right side of the bandage, however, is coupled via the bearing pin 16b and the blank 12b to the bandage part 2b on the right side of the bandage 2.

In Figure 9 the structure of a planetary gear 6 is shown.

• Der Hydraulikmotor 7 zum Antrieb der Oszillationsbewegung läuft, die Bandagenteile 2a, 2b sind nicht in Bewegung, d.h. beide Bandagenteile 2a, 2b stehen still. Folglich sind beide in Fig. 9 ersichtlichen Hohlräder 10a, 10b blockiert, da sie, wie schon beschrieben wurde, mit den Bandagen 2a, 2b verdrehstarr verbunden sind.

The synchronization of the unbalance moments is independent of the rotation of the bandage parts 2a, 2b. For ease of explanation, the following is assumed:

• The hydraulic motor 7 for driving the oscillatory movement is running, the bandage parts 2a, 2b are not in motion, ie both bandage parts 2a, 2b stand still. Consequently, both are in Fig. 9 apparent ring gears 10a, 10b blocked because they, as already described, are connected drehrehstarr with the bandages 2a, 2b.

In the planetary gear set 6a on the left side of the Fig. 9 is the drive torque, which is transmitted from the hydraulic motor 7 to the drive shaft 5a (sun shaft), passed through the sun gear 11a and the planetary gears 8a on the planet carrier 9. Case 3 (sun gear drives, bridge is output) of the elementary planetary gear set according to table 2 applies. The gear ratio i is accordingly 3.

The numbers of teeth of the wheels of the planetary gear 6 for calculating the gear ratios are listed in Table 1. Table 1: Number of teeth of the gears wheel 1 2 3 sun planet ring gear number of teeth 40 20 80

From the planetary carrier 9, the torque is now passed on via the planet gears 8b of the right stage to the right sun gear 11b and the drive shaft (sun shaft) 5b ( Figure 9 ). Since both planetary gear sets 6a, 6b have the same structure, the gear ratio i according to Table 2, Case 4 is therefore 1/3 for the right stage (planetary gear set 6b). This gives the torque transmission a total ratio of 1 (left sun 11a to right sun 11b).

3 Hohlrad Sonne Steg $$\left(\mathrm{z}\mathrm{1}+\mathrm{z}\mathrm{3}\right)/\mathrm{z}\mathrm{1}=\mathrm{3}$$

4 Hohlrad Steg Sonne $$\mathrm{Z}\mathrm{1}/\left(\mathrm{z}\mathrm{1}+\mathrm{z}\mathrm{3}\right)=\mathrm{1}/\mathrm{3}$$

Thus, if both bandage parts 2a, 2b rotate at the same speed - when driving straight ahead - or when resting, so there is no twisting of the bandage parts 2a, 2b to each other, the torque is transmitted as desired in the ratio 1: 1 from one side to the other , Table 2: Applications of planetary stages - elementary planetary set case fixed to the housing drive output Translation i 2 web ring gear Sun $$-\mathrm{<figure-callout\; id="1"\; label="z"\; filenames="imgf0001.png"\; state="\{\{state\}\}">z</figure-callout>}\mathrm{1}/\mathrm{<figure-callout\; id="3"\; label="z"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">z</figure-callout>}\mathrm{3}=-\mathrm{1}/\mathrm{2}$$

3 ring gear Sun web $$\left(\mathrm{z}\right)$$$$\left(\mathrm{}\mathrm{1}+\mathrm{<figure-callout\; id="3"\; label="z"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">z</figure-callout>}\mathrm{3}\right)/\mathrm{<figure-callout\; id="1"\; label="z"\; filenames="imgf0001.png"\; state="\{\{state\}\}">z</figure-callout>}\mathrm{1}=\mathrm{3}$$

4 ring gear web Sun $$\mathrm{Z}$$$$\mathrm{}\mathrm{1}/\left(\mathrm{<figure-callout\; id="1"\; label="z"\; filenames="imgf0001.png"\; state="\{\{state\}\}">z</figure-callout>}\mathrm{1}+\mathrm{<figure-callout\; id="3"\; label="z"\; filenames="imgf0002.png,imgf0003.png"\; state="\{\{state\}\}">z</figure-callout>}\mathrm{3}\right)=\mathrm{1}/\mathrm{3}$$

When rotating one bandage part 2a relative to the other 2b, it must be ensured that the imbalances 3 are rotated to the same extent.

• Der Bandagenteil 2a auf der einen Seite steht still, der Hydraulikmotor 7 läuft nicht. Kurz gesagt, das Hohlrad 10a der ersten Stufe (Planetensatz 6a), welches mit dem Bandagenteil 2a verbunden ist und das Sonnenrad 11a des ersten Planetensatzes 6a, der über die Antriebswelle 5a mit dem Hydraulikmotor 7 gekoppelt ist, stehen still. Folglich ist der Planetensatz 6a auf der einen Seite (in Fig. 9 auf der linken Seite) blockiert.

For ease of explanation, the following is taken:

• The bandage part 2a on the one hand stands still, the hydraulic motor 7 is not running. In short, the ring gear 10a of the first stage (planetary gear set 6a), which is connected to the bandage portion 2a and the sun gear 11a of the first planetary gear set 6a, which is coupled via the drive shaft 5a to the hydraulic motor 7, stand still. Consequently, the planetary gear set 6a is on one side (in Fig. 9 on the left).

The bandage part 2b on the other side is now mentally twisted by any angle.

The ring gear 10b of the planetary gear set 6b on the other (in Fig. 9 right) side is connected via the ring gear driver and the bearing pin 16b with the bandage part 2b. This now gives the rotation of the bandage part 2b on the planet gears 8b on the sun gear 11b on the right side. The common planet carrier 9 is, as already explained, blocked by the planetary gear set on the left side. Therefore, case 2 of the elementary planetary gear set from table 2 applies. The gear ratio i is therefore -0.5.

As already explained, the imbalance 3 must be rotated by the same angle as the bandage part 2a, 2b, in which it is mounted, in order to achieve a synchronization of the oscillatory movement in both band parts 2a, 2b.

Preferably, a two-stage planetary gear with a belt drive with reverse rotation and reciprocal translation can be used as a planetary gear 6.

The respective ring gears 10a, 10b of the planetary gear sets 6a, 6b are rotatably connected with bearing pins 16a, 16b, which are coaxially arranged in the adjacent rounds 12a, 12b of the bandage parts 2a, 2b, with the band parts 2a, 2b, wherein the bearing pins 16a, 16b at the same time the storage of the central drive pulleys 21 of the toothed belt drive 15a, 15b to drive the vibration exciter 30a, 30b form.

Alternatively, a multi-stage planetary gear with belt ratio not equal to the reciprocal of the transmission and without reversing direction can be used.

To a third planetary stage, which would accomplish a total ratio of 1 and direction reversal, by the guidance of the toothed belt 32c with omega wrap (see Fig. 10 ) and a transmission ratio of - 2 are dispensed with. The omega wrap means; that the toothed belt 15 c, the toothed belt pulleys 13 by more than 180 °, for example by about 200 ° to 210 °, in particular 205 °, as in Fig. 10 shown, encloses.

Due to the individual ratios of -0.5 in the planetary gear set and -2 in the toothed belt transmission 15 here is the overall ratio at 1.

The imbalances 3 are thus adjusted as required by the same angle as the twisted bandage parts 2a, 2b. The moments generated by the Oszillationsunwuchten are thus in each bandage part 2a, 2b in phase, regardless of the current position of the imbalances 3 to each other.

In the timing belt guide some fundamental innovations and advantageous change have been realized.

A belt drives two or more unbalance shafts. Would you drive out WO 82/201903 transferred to a split drum 20, eight pulleys and four belts would be needed.

In contrast to the previous undivided constructions ( WO 82/201903 ), which provide a separate toothed belt drive for each unbalanced shaft, are driven here by a belt, preferably a toothed belt 32, both imbalances 3 of a bandage part 2a, 2b. As a result, each of a toothed belt 32 and a drive pulley per bandage half can be omitted.

As already described before, a gear ratio of -2 is realized in the timing belt guide. This was done by means of an omega wrap of the toothed belt 32 according to Fig. 10 reached. For this, the large toothed pulleys 13 have twice the number of teeth compared to the small drive pulley 21.

By the deflection of the small toothed disc 21, the direction of rotation is changed, which leads to the required negative transmission ratio.

By the required translation of the toothed belt drive of -2 is preferably a large toothed disc 13 can be used, in which also a part of the imbalance 3 can be realized.

Since the toothed belt pulley 13 for screwing the unbalance plates 14 must be drilled anyway, additional holes 35 can be attached to produce a portion of the required imbalance 3 on the opposite side of the imbalance weights in the form of imbalance plates 14 (negative imbalance). Another advantage is the lower moment of inertia of the toothed belt pulley 13 due to the weight reduction, which leads to a faster run-up when starting the drive.

The remaining portion of the imbalance 3, the lateral unbalance plates 14 and deliver, for example, the nine screws 18 as imbalance weight (positive imbalance), whereby the imbalance plates 14 are preferably attached to both sides of the pulleys 13 ( Figure 10 ).

The already required toothed belt pulley 13 therefore also serves as imbalance 3. The side of the pulley 13 arranged unbalance plates 14 are screwed directly to the respective toothed belt pulley 13. The screws 18 form an additional imbalance weight. The holes or holes 35 on the opposite side of the screws 18 thereby form a negative imbalance.

In Figure 10 the two laterally mounted unbalance plates 14 are shown in the assembled position with the toothed belt 32 on. The outer contour of the imbalance plates 14 is designed such that the inclined edge 14a on the sides of the imbalance plates 14 with the short strand 32a of the toothed belt 32 is exactly aligned. This is a way to visually check the correct 180 ° offset of the unbalance 3 based on the position of the belt 32.

The angles of the sloping flanks 14a of the unbalance plates 14 correspond to the angle of the belt 32 at the omega-wrapped side in FIG Fig. 10 shown position.

The unbalance plates 14 are preferably arranged on both sides of the toothed belt pulley in the same position. With the thickness of the imbalance plates 14, the mass of the imbalance 3 can be changed, as well as with the number of screws 18 or the size of the holes 35th

So far, the required belt tension of the toothed belt 32 has been made either by means of an additional idler pulley, or only selected, measured toothed belts 32 having a precisely tolerated length have been used.

In the in the FIGS. 10 and 11 As shown, the belt tension is adjusted by continuously changing the axial distance between the drive shaft 5a, 5b and the axis of the trunnion 20a, 20b. This is done by turning the eccentrically mounted bearing pin 20a, 20b on the unbalance flange 19 (FIG. Figure 11 ) reached.

The rotation of the eccentric unbalance flange 19 with the bearing pin 20a, 20b for tensioning the toothed belt 15c is done by turning an eccentric adjusting pin 17 (FIG. Fig. 10 ). This consists of two mutually eccentric cylinders and a hexagon for attaching a key. The eccentric adjusting bolt 17 is provided for rotating the eccentric unbalance flange 19.

Due to the eccentricity, the unbalance flange 19 is rotated relative to the blank 12a, 12b when the adjusting bolt 17 is rotated.

It is thus possible to tension the belt 32 by means of an eccentrically displaceable journal arrangement.

The cantilever bearing journal 20a, 20b serves to receive a roller bearing 34 for the toothed belt pulley 13. The roller bearing 34 is arranged centric to the radial belt force and centrifugal force of the imbalances 3.

Fig. 12 shows a perspective view of the toothed belt pulley 13 without toothed belt 32nd

Claims (16)

1. A compaction device, comprising at least one traveling drum (2) rotatable about a drum shaft (1), coupled vibration exciters (30a,30b) generating an oscillation torque about the drum shaft (1), said vibration exciters having unbalanced masses (3) rotating out of phase by 180 degrees in the same direction of rotation, and having a drive shaft (5a,5b) running coaxial to the drum shaft (1) for driving the vibration exciters (30a, 30b),
   characterized in that
   the drum (2) with the drive shaft (5a;5b) is divided at least once and that each drum part (2a,2b) comprises at least two coupled vibration exciters (30a,30b) mounted in the drum (2) at a distance from the drum shaft (1), wherein the vibration exciters (30a) of one drum part (2a) are coupled to the vibration exciters (30b) of another drum part (2b) in such a manner that the vibration exciters (30a,30b) of all drum parts (2a,2b) oscillate in synchronism also in case of a turning of the drum parts (2a,2b) relative to each other.
2. The compaction device according to claim 1, characterized in that the drive shafts (5a,5b) for the vibration exciters (30a,30b) of the individual drum parts (2a,2b) are mechanically coupled or via a control means are adjusted to be in-phase.
3. The compaction device according to claim 1 or 2, characterized in that the drive shafts (5a,5b) for the vibration exciters (30a,30b) of the adjacent drum parts (2a,2b) are mechanically coupled via a transmission (6) and said transmission (6) is operative to transmit the rotation and respectively the drive torque of a drive shaft (5a) with correct phase to the following drive shaft (5b) of the drum part (2a).
4. The compaction device according to claim 3, characterized in that the transmission for coupling the drive shaft parts (5a,5b) is a planetary gear transmission (6) or a spur gear transmission or a bevel gear transmission.
5. The compaction device according to any one of claims 1 to 4, characterized in that the drum (2) is of a two-part design and each drum part (2a,2b) comprises a traveling drive (7a,7b) of its own, the drum parts (2a,2b) being connected to each other in a manner allowing them to be turned coaxially relative to each other.
6. The compaction device according to claim 4 or 5, characterized in that the planetary gear transmission (6) comprises at least two planetary gear sets (6a,6b).
7. The compaction device according to claim 6, characterized in that the planetary gear transmission (6) comprises two planetary gear sets (6a, 6b) having a common planetary carrier (9), wherein ring gears (10a, 10b) of the planetary gear sets (6a,6b) are respectively connected to a drum part (2a,2b) for common rotation therewith, and the respective drive shafts (5a,5b) are connected to the respective sun gears (11a, 11b) of the planetary gear sets (6a,6b).
8. The compaction device according to any one of claims 1 to 7, characterized in that the drive shaft (5a,5b) of each drum part (2a,2b) is operative to drive, via a transmission, the at least two vibration exciters (30a,30b).
9. The compaction device according to claim 8, characterized in that the drive for driving the unbalanced masses (3) is a belt transmission or a chain drive.
10. The compaction device according to any one of claims 3 to 9, characterized in that the drive for driving the vibration exciters (30a,30b) is a toothed-belt transmission (15a,15b) comprising a toothed belt (32) for driving toothed-belt pulleys (13) coupled with unbalanced masses (3).
11. The compaction device according to any one of claims 9 or 10, characterized in that the drive is a belt transmission with a belt guiding arrangement allowing for reversal of the direction of circulation and for a reciprocal transmission ratio toward the planetary gear transmission (6).
12. The compaction device according to any one of claims 9 to 11, characterized in that a multi-stage planetary gear transmission (6) and a belt transmission without reversal of rotational direction and without reciprocal transmission ratio toward the planetary gear transmission (6) are provided.
13. The compaction device according to any one of claims 10 to 12, characterized in that the vibration exciters (30a,30b) comprise unbalanced masses (3) and said unbalanced masses (3) comprise unbalanced plates (14) being laterally fastened to toothed-belt pulleys (13) of the toothed-belt transmission (15a,15b) and having a radially outward flank (14) which in a predetermined starting position is in alignment with the toothed belt (32) of the toothed-belt transmission (15a,15b) if the rotational angle displacement between the two toothed-belt pulleys (13) driven by the toothed-belt transmission (15a,15b) corresponds to the desired value.
14. The compaction device according to any one of claims 9 to 13, characterized in that a belt tensioning device is operative to tension the belt (32) for driving the unbalanced masses (3) and respectively of the pulleys (13) with the aid of an eccentrically displaceable bearing pin (20a, 20b).
15. The compaction device according to any one of claims 9 to 14, characterized in that the belt transmission (15a,15b) comprises pulleys (13) which are coaxial and concentric with the rotational axis of the unbalanced masses (3) and whose weight distribution does not extend with rotational symmetry with respect to the rotational axis of the unbalanced masses (3).
16. A method for the compacting of ground by means of a drum (2) of a compacting device, said drum being rotatable about a drum shaft (1), wherein, with the aid of coupled vibration exciters (30a,30b) comprising unbalanced masses (3) rotating at a distance from the drum axis (1), a moment of rotation that oscillates about the drum axis (1) is generated, the unbalanced masses (3) being driven to rotate out of phase by 180 degrees in the same direction of rotation, characterized by the use of a divided drum (2) with at least two drum halves (2a, 2b), in which the unbalanced masses (3) of the vibration exciters (30a, 30b) in each part (2a,2b) of the drum (2) are rotated by the same angle with respect to the phase position as in the turning of the drum halves (2a,2b) relative to each other, so that a synchronization of the oscillatory movement in all drum parts (2a,2b) is obtained even if the drum parts (2a, 2b) have been turned relative to each other.

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