Compaction roller for a soil compactor

Description

[0001] The present invention relates to a compactor roller for a soil compactor, comprising a roller shell rotatable about a roller rotation axis and enclosing a roller interior, and an oscillation / vibration arrangement arranged in the roller interior.

[0002] A compaction roller for a soil compactor according to the preamble of claim 1 is known from JP 2004-223313 A. The two oscillation / vibration units of the oscillation / vibration arrangement of this known compaction roller each comprise a first unbalanced mass component rigidly mounted on an oscillation / vibration shaft rotatable about a respective oscillation / vibration axis of rotation, and comprise a second unbalanced mass component pivotably mounted on an outer circumferential surface of the oscillation / vibration shaft about the respective oscillation / vibration axis of rotation with respect to the respective first unbalanced mass component.

[0003] Depending on the direction of rotation of the two unbalanced mass components around their respective oscillation / vibration axes, the centers of mass of each of the two oscillation / vibration units are arranged with a phase shift of 180° relative to the respective oscillation / vibration axis, so that a resulting unbalance moment in each of the oscillation / vibration units results from the difference of the unbalance moments of the two unbalanced mass components, or they are arranged on the same side relative to the respective oscillation / vibration axis, i.e., without a phase shift relative to each other, so that a resulting unbalance moment results from the sum of the unbalance moments of the respective unbalanced mass components.Furthermore, depending on the direction of rotation, the centers of mass of the unbalance masses comprising the two unbalance mass components of the two oscillation / vibration units are either angularly offset by 180° from each other or have no phase offset from each other, so that, depending on the direction of rotation, it is possible to switch between a vibration operation, in which the centrifugal forces acting on the center of mass of both oscillation / vibration units are equal in magnitude and direction, thus creating a total centrifugal force essentially orthogonal to the roller axis of rotation, or an oscillation operation, in which the two centrifugal forces arising at the oscillation / vibration units are equal in magnitude but opposite in direction, so that a resulting torque acting tangentially or circumferentially is created and the compressor roller is periodically accelerated back and forth around the roller axis of rotation.The switching between the two operating states is achieved by pivoting the respective second unbalanced mass part of the two oscillation / vibration units relative to the respective first unbalanced mass part about the associated oscillation / vibration axis of rotation at an angle of 180°, so that in each of the two end positions of the second unbalanced mass parts their center of mass lies on a common radial line with the center of mass of the respective associated first unbalanced mass part.

[0004] From DE 10 2012 201 443 A1, a compressor roll is known in which an oscillation / vibration arrangement is provided inside the roll. The oscillation / vibration arrangement comprises a vibration assembly that can be driven to rotate about a roll axis of rotation of the compressor roll and has two vibrating unbalanced masses arranged axially apart from each other, with their centers of mass eccentric to the roll axis of rotation. The oscillation / vibration arrangement further comprises an oscillation arrangement with two oscillating unbalanced masses rotatable about oscillation axes that are eccentric to the roll axis of rotation and arranged at an angular distance of 180° from it. The centers of mass of the two oscillating unbalanced masses rotatable about the oscillation axes of rotation have a phase shift of 180° to each other.Each oscillating unbalance mass has a base unbalance mass that is rotationally fixed to its respective oscillation shaft and a variation unbalance mass that can move circumferentially around its associated oscillation axis of rotation with respect to the base unbalance mass between two end positions along an associated guide track. By changing the direction of rotation and thus moving the variation unbalance masses between their respective end positions, the position of the respective center of mass with respect to the associated oscillation axis of rotation is changed. This change in the position of the two centers of mass allows the oscillation arrangement to be used at different oscillation frequencies or with different oscillation amplitudes.

[0005] The object of the present invention is to provide a compaction roller for a soil compactor with an oscillation / vibration arrangement in which a change in the unbalanced moment occurring when switching between an oscillation operation and a vibration operation can be achieved with a compact design of the oscillation / vibration units.

[0006] According to the invention, this problem is solved by a compactor roller for a soil compactor, comprising a roller shell rotatable about a roller axis of rotation and enclosing a roller interior, an oscillation / vibration arrangement arranged in the roller interior, wherein the oscillation / vibration arrangement comprises: a first oscillation / vibration unit with at least one first unbalanced mass that can be driven to rotate about a first oscillation / vibration axis of rotation, wherein the at least one first unbalanced mass comprises a first unbalanced mass part and a second unbalanced mass part that is movable between two end positions about the first oscillation / vibration axis of rotation with respect to the first unbalanced mass part, wherein when the at least one first unbalanced mass is rotated about the first oscillation / vibration axis of rotation in a first direction of rotation, the second unbalanced mass part of the at least one first unbalanced mass is in its first end position, and when the at least one first unbalanced mass is rotated about the first oscillation / vibration axis of rotation in a second direction of rotation opposite to the first direction of rotation, the second mass part of the at least one first unbalanced mass is in its second end position.wherein, when the second unbalance mass part of the at least one first unbalance mass moves between its first end position and its second end position, the center of mass of the second unbalance mass part of the at least one first unbalance mass moves at a first predetermined angle about the first oscillation / vibration axis of rotation, a second oscillation / vibration unit with at least one second unbalance mass that can be driven to rotate about a second oscillation / vibration axis of rotation, wherein the at least one second unbalance mass comprises a first unbalance mass part and a second unbalance mass part that is movable about the second oscillation / vibration axis of rotation between two end positions with respect to the first unbalance mass part,wherein, when the at least one second unbalanced mass is rotated about the second oscillation / vibration axis of rotation in the first direction of rotation, the second unbalanced mass part of the at least one second unbalanced mass is in its first end position, and when the at least one second unbalanced mass is rotated about the second oscillation / vibration axis of rotation in the second direction of rotation, the second unbalanced mass part of the at least one second unbalanced mass is in its second end position, wherein, when the second unbalanced mass part of the at least one second unbalanced mass moves between its first end position and its second end position, a center of mass of the second unbalanced mass part of the at least one second unbalanced mass moves at a second predetermined angle about the second oscillation / vibration axis of rotation, , wherein, when the second unbalanced mass component of the at least one first unbalanced mass is positioned in its first end position, and when the second unbalanced mass component of the at least one second unbalanced mass is positioned in its first end position, the center of mass of the at least one first unbalanced mass and the center of mass of the at least one second unbalanced mass have essentially no phase offset relative to each other, and a first centrifugal force acting at the center of mass of the at least one first unbalanced mass and a second centrifugal force acting at the center of mass of the at least one second unbalanced mass are essentially directed in the same direction relative to each other and have an essentially equal first centrifugal force magnitude,wherein, when the second unbalanced mass component of the at least one first unbalanced mass is positioned in its second end position, and when the second unbalanced mass component of the at least one second unbalanced mass is positioned in its second end position, the center of mass of the at least one first unbalanced mass and the center of mass of the at least one second unbalanced mass have a phase shift of approximately 180° relative to each other, and the first centrifugal force acting at the center of mass of the at least one first unbalanced mass and the second centrifugal force acting at the center of mass of the at least one second unbalanced mass are directed substantially oppositely to each other and have a substantially equal second centrifugal force magnitude.

[0007] A compact design is made possible according to the principles of the present invention by providing a first guide track with a radially inwardly oriented guide track surface normal on the first unbalance mass part of the at least one first unbalance mass for moving the second unbalance mass part of the at least one first unbalance mass, which is supported radially outwardly on the first guide track, between its first end position and its second end position, and by providing a second guide track with a radially inwardly oriented guide track surface normal on the first unbalance mass part of the at least one second unbalance mass for moving the second unbalance mass part of the at least one second unbalance mass, which is supported radially outwardly on the second guide track, between its first end position and its second end position.

[0008] By supporting the respective second unbalance mass component radially outwards on guide tracks oriented radially inwards, it becomes possible to shift the second unbalance mass components, or rather their center of mass, comparatively far radially outwards, so that even second unbalance mass components with comparatively low mass contribute to a comparatively large unbalance moment due to the larger radial distance to the respective oscillation / vibration axis of rotation and are thus able to bring about the compensation or addition of the individual unbalance moments of the unbalance mass components to the desired extent for the switching behavior.

[0009] According to the invention, the first predetermined angle can be less than 180° or greater than 180°, and / or the second predetermined angle can be less than 180° or greater than 180°.

[0010] In the inventive design of a compressor roller, a compact design of the respective unbalanced mass is made possible by a reversal angle other than 180°, in particular a reversal angle of less than 180°.

[0011] In order to ensure that, even with such a comparatively short movement path of a respective second unbalance mass component, the defined positions of the mass centers of the two unbalance masses are maintained with a phase offset of 180° or 180° in the various directions of rotation.To achieve a phase shift without any offset between them, it is proposed that, when the second unbalanced mass component of the at least one first unbalanced mass is positioned in its second end position, the center of mass of the second unbalanced mass component of the at least one first unbalanced mass and a center of mass of the first unbalanced mass component of the at least one first unbalanced mass do not lie on a common radial line intersecting the first oscillation / vibration rotation axis, or / and that, when the second unbalanced mass component of the at least one second unbalanced mass is positioned in its second end position, the center of mass of the second unbalanced mass component of the at least one second unbalanced mass and a center of mass of the first unbalanced mass component of the at least one second unbalanced mass do not lie on a common radial line intersecting the second oscillation / vibration rotation axis.

[0012] In particular, it can be provided that, when the second unbalanced mass part of the at least one first unbalanced mass is positioned in its first end position and when the second unbalanced mass part of the at least one first unbalanced mass is positioned in its second end position, the center of mass of the second unbalanced mass part of the at least one first unbalanced mass and the center of mass of the first unbalanced mass part of the at least one first unbalanced mass lie circumferentially on both sides of a radial line intersecting the first oscillation / vibration rotation axis.or / and that, when the second unbalanced mass component of the at least one second unbalanced mass is positioned in its first end position and when the second unbalanced mass component of the at least one second unbalanced mass is positioned in its second end position, the center of mass of the second unbalanced mass component and the center of mass of the first unbalanced mass component of the at least one second unbalanced mass lie circumferentially on both sides of a radial line intersecting the second oscillation / vibration rotation axis.

[0013] To ensure a suitable change in the unbalance moments when flipping the second set of unbalanced masses, it is further proposed that if the first predetermined angle and the second predetermined angle are less than 180°, the first predetermined angle is greater than the second predetermined angle, and if the first predetermined angle and the second predetermined angle are greater than 180°, the first predetermined angle is less than the second predetermined angle.

[0014] Since, for switching between oscillation and vibration operation, the second unbalanced mass components only need to move over a limited angular range of approximately 180° around the respective oscillation / vibration axis of rotation, it is further proposed for a compact design that the first guide track extends only over a partial circumferential area around the first oscillation / vibration axis of rotation, and that the second guide track extends only over a partial circumferential area around the second oscillation / vibration axis of rotation.

[0015] In order to easily achieve the same degree of switching between different total unbalance moments in the two oscillation / vibration units, it is further proposed that a radial distance of the first guide track to the first oscillation / vibration axis of rotation essentially corresponds to a radial distance of the second guide track to the second oscillation / vibration axis of rotation.

[0016] In order to eliminate the influence of centrifugal force-induced friction as far as possible during movement between the different end positions, it is further proposed that the second unbalance mass part of the at least one first unbalance mass comprises at least one first rolling body which rolls along the first guide track during movement between the first end position and the second end position, and that the second unbalance mass part of the at least one second unbalance mass comprises at least one second rolling body which rolls along the second guide track during movement between the first end position and the second end position.

[0017] In order to provide different imbalance moments for the two second unbalance mass components, the number of first rolling bodies can differ from the number of second rolling bodies.

[0018] To keep the number of differently designed components as low as possible, all first rolling bodies and all second rolling bodies can be constructed identically to each other.

[0019] In a design that is advantageous for greater freedom regarding the switching behavior, at least one first rolling element can differ from at least one second rolling element.

[0020] In order to achieve a symmetrical effect of the two oscillation / vibration units, it is proposed that the first oscillation / vibration axis of rotation and the second oscillation / vibration axis of rotation are arranged essentially parallel to each other and to the roller axis of rotation, or / and that the first oscillation / vibration axis of rotation and the second oscillation / vibration axis of rotation have an angular distance of approximately 180° with respect to the roller axis of rotation.

[0021] The first unbalance mass component of the at least one first unbalance mass can be carried on a first oscillation / vibration shaft that can be driven to rotate about the first oscillation / vibration axis of rotation, and / or the first oscillation / vibration shaft can provide at least a part of the first unbalance mass component of the at least one first unbalance mass, and the first unbalance mass component of the at least one second unbalance mass can be carried on a second oscillation / vibration shaft that can be driven to rotate about the second oscillation / vibration axis of rotation, and / or the second oscillation / vibration shaft can provide at least a part of the first unbalance mass component of the at least one second unbalance mass.

[0022] In order to put the various oscillation / vibration units into operation, it is proposed that the oscillation / vibration arrangement includes an oscillation / vibration drive, and that the at least one first unbalanced mass of the first oscillation / vibration unit and the at least one second unbalanced mass of the second oscillation / vibration unit can be driven by the oscillation / vibration drive to rotate in the same direction and at the same speed.

[0023] In order to provide a sufficiently large mass for the oscillation / vibration units, it is proposed that the first oscillation / vibration unit comprises two first unbalanced masses arranged at a distance from each other in the direction of the first oscillation / vibration axis of rotation, preferably of identical construction, or / and that the second oscillation / vibration unit comprises two second unbalanced masses arranged at a distance from each other in the direction of the second oscillation / vibration axis of rotation, preferably of identical construction.

[0024] In order to achieve a change in the magnitude of the force acting on a compressor roller when switching between oscillation and vibration operation, i.e., when changing the direction of rotation of the unbalanced masses, it is further proposed that the second centrifugal force value be greater than the first centrifugal force value.

[0025] This can be achieved, for example, by ensuring that an imbalance moment of the first unbalance mass component of the at least one first unbalance mass essentially corresponds to an imbalance moment of the second unbalance mass component of the at least one second unbalance mass, and that an imbalance moment of the first unbalance mass component of the at least one second unbalance mass essentially corresponds to an imbalance moment of the second unbalance mass component of the at least one first unbalance mass, where each imbalance moment is defined as: U = m × r , where: Uda's unbalance moment of a respective unbalance mass part is, my inertial mass of the unbalance mass part acting in the center of mass of a respective unbalance mass part is, and purely radial distance of the center of mass of a respective unbalance mass part to the associated oscillation / vibration axis of rotation is.

[0026] Furthermore, particularly taking into account the comparatively short movement paths of the respective second unbalance mass parts between their end positions in order to achieve the total unbalance moments to be set on the two unbalance masses, it can be provided that the first unbalance mass part of the at least one first unbalance mass has a larger unbalance moment than the first unbalance mass part of the at least one second unbalance mass, and that the second unbalance mass part of the at least one first unbalance mass has a smaller unbalance moment than the second unbalance mass part of the at least one second unbalance mass.

[0027] The invention further relates to a soil compactor with at least one compaction roller having the structure described above according to the invention.

[0028] The present invention is described in detail below with reference to the accompanying figures. These show: Fig. 1 a side view of a soil compactor with a compaction roller; Fig. 2 a longitudinal section view of a compaction roller with an oscillation / vibration arrangement comprising two oscillation / vibration units; Fig. 3 an axial view of an unbalanced mass of the first of the two oscillation / vibration units; Fig. 4 an axial view of an unbalanced mass of the second of the oscillation / vibration units; Fig. 5 a schematic representation of the compaction roller of the Fig. 2 in axial view in an oscillation operation of the oscillation / vibration arrangement; Fig. 6 one of the Fig. 5 corresponding view in a vibration operation of the oscillation / vibration arrangement.

[0029] In Fig. 1 A soil compactor is generally designated by 10. The soil compactor 10, which can be used, for example, for compacting asphalt, soil, gravel, or other bound or unbound soil material, comprises a rear carriage 12 with a cab 14 mounted on it for an operator. A drive unit is provided on the rear carriage 12, by which drive wheels 15 arranged on the rear carriage 12 can be driven to move the soil compactor 10 in a forward or reverse direction.

[0030] A front carriage 18, mounted on a frame 16, is pivotably supported on the rear carriage 12. The soil compactor 10 can be steered by pivoting the front carriage 18 about an approximately vertical axis relative to the rear carriage 12. A compaction roller 20 is mounted on the frame 16 of the front carriage 18 about a Fig. 2 The depicted roller axis of rotation W is rotatably mounted. The compaction roller 20 can itself be driven to rotate about the roller axis of rotation W, or alternatively, it can be mounted on the frame 16 of the front carriage 18 so that it can rotate essentially freely about the roller axis of rotation B. During a compaction process, the compaction roller 20 rolls over the substrate 26 with an outer surface 22 of a roller shell 24 enclosing a roller interior 23.

[0031] Inside the roller chamber 23 of the in Fig. 2 The compactor roller 20 shown in longitudinal section is equipped with an oscillation / vibration arrangement, generally designated 28. As described in detail below, the oscillation / vibration arrangement 28 allows a force to be exerted on the compactor roller 20 or its roller shell 24 to influence the compaction behavior. In a vibration operation described below, this force is essentially orthogonal to the roller's axis of rotation W, and the direction of the force rotates around the roller's axis of rotation W. This results in the compactor roller 20 operating in a vibration mode. Due to the direction of rotation around the roller's axis of rotation W, the compactor roller 20 is periodically accelerated upwards and downwards, and thus periodically impacts or is pressed against the substrate 22 to be compacted.In oscillation mode of the oscillation / vibration arrangement, the force exerted on the compressor roller 20 acts tangentially or circumferentially, so that the roller shell 24 is periodically accelerated back and forth circumferentially around the roller rotation axis W, thus creating a walking effect in compression mode.

[0032] The oscillation / vibration arrangement 28 comprises two oscillation / vibration units 30, 32. Each of the oscillation / vibration units 30, 32 can be driven by an oscillation / drive 34 to rotate about a respective oscillation / vibration axis D1 or D2. The oscillation / vibration drive 34 can, for example, include a hydraulic motor 36, which drives the two oscillation / vibration units 30, 32 via a belt drive mechanism 38 to rotate about their respective oscillation / vibration axes D1 and D2 in the same direction and at the same speed.

[0033] The first oscillation / vibration arrangement 30 comprises a first oscillation / vibration shaft 40, which is rotatably supported, for example, at its two axial end regions on support disks 42, 44 attached to an inner circumferential surface of the roller shell 24. Correspondingly, the second oscillation / vibration unit 32 comprises a second oscillation / vibration shaft 46 rotatably supported on the two support disks 42, 44.

[0034] On the first oscillation / vibration shaft 40 of the first oscillation / vibration unit 30, two first unbalanced masses 50, 50', preferably of substantially identical construction, are mounted at an axial distance from each other. Likewise, on the second oscillation / vibration shaft 46 of the second oscillation / vibration unit 32, two second unbalanced masses 52, 52', preferably of substantially identical construction, are mounted at an axial distance from each other. The arrangement is such, for example, that each of the two oscillation / vibration units 30, 32 has one unbalanced mass 50, 50' or 52, 52' in the same axial range as the other of the two oscillation / vibration units 30, 32. Furthermore, the Fig. 2 It is evident that the two oscillation / vibration units 30, 32 are arranged such that their respective oscillation / vibration axes of rotation D1, D2 extend essentially parallel to the roller axis of rotation W and are also equidistant from it. Furthermore, the two oscillation / vibration units 30, 32, or rather their oscillation / vibration axes of rotation D1, D2, are angularly separated from each other by approximately 180° with respect to the roller axis of rotation W, so that the two oscillation / vibration axes of rotation D1, D2 are diametrically opposed to each other with respect to the roller axis of rotation W.

[0035] With regard to the Fig. 3 und 4 The following section describes in detail the first unbalance masses 50, 50' and the second unbalance masses 52, 52' of the two oscillation / vibration units 30, 32, whereby, due to the already mentioned identical design of the respective unbalance masses 50, 50' and 52, 52', reference is made only to the first unbalance mass 50 of the first oscillation / vibration unit 30 and the second unbalance mass 52 of the second oscillation / vibration unit 32.

[0036] The in Fig. 3 The first unbalanced mass 50, shown in axial view and carried on the first oscillation / vibration shaft 40, comprises a first unbalanced mass part 54, which is rotationally fixed to the first oscillation / vibration shaft 40, for example, by screws and / or by material bonding. The first unbalanced mass part 54 has an unbalanced mass element 56 fixed to the first oscillation / vibration shaft 40 and a guide track element 58 fixedly connected to the unbalanced mass element 56. The unbalanced mass element 56 and the guide track element 58 define a receiving space 60 for a second unbalanced mass part 62 of the first unbalanced mass 50, which is movable relative to the first unbalanced mass part 54 of the first unbalanced mass 50.

[0037] In the illustrated embodiment, the second unbalance mass component 62 comprises a substantially cylindrical, i.e., roller-like, first rolling element 64, which, in the rotational state of the first unbalance mass 50, is subjected to radial outward centrifugal force and pressed against a radially inwardly oriented first guide track 66 provided on the guide track element 58. The radially inwardly oriented first guide track 66 maintains a substantially constant circumferential distance around the first oscillation / vibration axis D 1, such that a radially inwardly oriented guide track surface normal N 1 of the first guide track 66 is oriented substantially radially inward with respect to the first oscillation / vibration axis D 1. In the axial direction, the receiving space 60 can be closed, for example, by disc-like cover elements to prevent the rolling element from axially falling out of the receiving space 60.These cover elements thus provide a part of the respective first unbalance mass part 54 and contribute to its mass or to its unbalance moment.

[0038] The rolling body 64, which essentially provides the second mass component 62, is movable along the first guide track 66 in the receiving space 60 between two end positions. Fig. 3 The first rolling element 64 is positioned in its second end position, in which it is supported circumferentially on the unbalance mass element 56 and is positioned near an unbalance mass section 68 of the unbalance mass element 56. A large part of the mass of the unbalance mass element 56 is provided in the unbalance mass section 68, so that during the Fig. 3 In the depicted positioning of the second unbalanced mass part 62 in its second end position, the center of mass of the first unbalanced mass 50 is positioned essentially above the first oscillation / vibration axis of rotation D 1, and thus the centrifugal force acting in this state when the first unbalanced mass 50 rotates is essentially directed upwards.

[0039] After the second unbalanced mass part 62 moves along the first guide track 66, the second unbalanced mass part 62 comes into its position in Fig. 3 The first end position, shown with a dashed line, in which the first rolling element 64 of the second unbalance mass part 62 is supported circumferentially on a support section 70 of the unbalance mass element 56. Even in this state, the following applies: Fig. 3 In the depicted rotational positioning of the first unbalanced mass 50, its center of mass is essentially located above the first oscillation / vibration axis of rotation D 1. However, due to the fact that a large part of the total mass of the first unbalanced mass 50 is now positioned in the lower region of the first unbalanced mass 50, its center of mass has a smaller radial distance to the first oscillation / vibration axis of rotation D 1. Therefore, the unbalance moment present in this state or rotational positioning of the first unbalanced mass 50 is lower than an unbalance moment that the first unbalanced mass 50 would have if the second unbalanced mass part 62 were in its position in Fig. 1 The second end position shown above is therefore the centrifugal force occurring when positioning the second unbalanced mass part 62 in its second end position, compared to a state in which the second mass part 62 is in its first end position, supported circumferentially by the unbalanced mass section 68.

[0040] In Fig. 3 It can be seen that when the second unbalanced mass part 62 is positioned in its second end position, the center of mass M 12 of the second unbalanced mass part 62 and the center of mass M 11 of the first unbalanced mass part 54 of the first unbalanced mass 50 or 50' are offset from each other in the circumferential direction and therefore do not lie on a common radial line that intersects the first oscillation / vibration axis of rotation D1. Such a radial line intersecting the first oscillation / vibration axis of rotation D1 is shown in the Fig. 3 The radial line R, which is recognizable and approximately corresponds to a vertical line in this state of rotation, is illustrated. The centers of mass M11 and M12 lie on either side of this radial line R in the circumferential direction.

[0041] Even after the second unbalanced mass component moves into its first end position, the centers of mass M11 and M12 lie circumferentially on both sides of the radial line R, since during movement between the second end position and the first end position, the first unbalanced mass component 62, or rather its center of mass M12, moves along the associated guide track 66 around the first oscillation / vibration axis of rotation D1 at an angle W1 of less than 180°. Therefore, in each of the two end positions of the second unbalanced mass component 62 of the respective first unbalanced mass 50, 50', the center of mass is located in the Fig. 3 The depicted state of rotation shows the center of mass of the unbalanced mass 50 or 50' on the radial line R and above the first oscillation / vibration axis of rotation D 1, but with different radial distances to this, so that when positioning the second unbalanced mass part 62 in its second end position, a larger unbalanced moment of the respective first unbalanced mass 50 or 50' results than when positioning the second unbalanced mass part 62 in its second end position.

[0042] The Fig. 4 Figure 1 shows the construction of the second unbalanced mass 52, which is essentially the same as the construction of the first unbalanced mass 50. The second unbalanced mass 52 has a first unbalanced mass part 72, which is fixed against rotation on the second oscillation / vibration shaft 46. This first unbalanced mass part 72 is in turn formed with an unbalanced mass element 74 and a guide track element 78, which together with the first element defines a receiving space 76. A second guide track 80, oriented radially inwards, is formed on the guide track element 78. The normal N2 of the guide track surface is directed essentially radially inwards towards the second oscillation / vibration axis of rotation D2.

[0043] In In the receiving space 76, a second unbalance mass component 82 of the second unbalance mass 52 is movably mounted relative to the first unbalance mass component 72 in the circumferential direction about the second oscillation / vibration axis of rotation D 2. The second unbalance mass component 82 of the second unbalance mass 52 comprises, for example, two second rolling elements 84, 86, which are identical in construction to each other and also to the first rolling element 64 of the second unbalance mass component 62 of the first unbalance mass 50. The second rolling elements 84, 86 can roll along the second guide track 80 in the receiving space 76 between the in Fig. 4 the second end position of the same or of the second unbalance mass part 82 shown below, in which the second rolling bodies 84, 86 are supported on an unbalance mass section 88 of the unbalance mass element 74, and a in Fig. 4 move to the first end position shown above, in which the second rolling bodies 84, 86 are supported in the circumferential direction on a support section 90 of the unbalance mass element 74 of the first unbalance mass part 72 of the second unbalance mass 52. In In the axial direction, the receiving space 76 can, for example, be closed off by disc-like cover elements to prevent the rolling body from falling out of the receiving space 76 axially. These cover elements thus provide part of the respective first unbalance mass component 72 and contribute to its mass or its unbalance moment.

[0044] When positioning the second rolling elements 84, 86 of the second unbalance mass part 82 of the second unbalance mass 52 in the in Fig. 4 In the second end position shown below, the center of mass of the second unbalanced mass 52 lies in the position shown below. Fig. 4 The depicted rotational state of the second unbalanced mass 52 is essentially located under the second oscillation / vibration axis of rotation D 2. Since a large part of the mass of the second unbalanced mass part 52 is located under the second oscillation / vibration axis of rotation D 2 and approximately in the same circumferential region, the second unbalanced mass 52 exhibits a comparatively large unbalance moment in this state, because the center of mass of the second unbalanced mass 52 has a comparatively large radial distance to the second oscillation / vibration axis of rotation D 2 due to this mass distribution.

[0045] Is the second unbalance mass part 82 of the second unbalance mass 52 in its in Fig. 4 In the first end position shown above, a larger part of the mass of the second unbalanced mass 52 is moved upwards. This results in the center of mass of the second unbalanced mass 52 or 52' ​​being located in this state. Fig. 4 The rotational positioning shown is essentially above the second oscillation / vibration axis D 2, but has a smaller radial distance to it than when the second unbalanced mass part 82 is positioned in the second end position. This means that when the second mass part 82 is positioned in the first end position, the centrifugal force acting at the center of mass is smaller than when the second mass part 82 is positioned in the second end position.

[0046] This switching behavior is also achieved for the respective second unbalance mass 52 or 52' ​​by the fact that, in both end positions of the second unbalance mass part 82, a center of mass M 22 of the second unbalance mass part 82 and a center of mass M 21 of the first unbalance mass part 72 are offset from each other circumferentially and thus do not lie on a common radial line intersecting the second oscillation / vibration axis of rotation D 2, but rather on either side of the radial line R, which in this rotational state essentially corresponds to a vertical direction. This is also achieved by the fact that, during movement between the two end positions, the second unbalance mass part 82 of the second unbalance mass 52 or 52', or rather its center of mass M 22, moves about the second oscillation / vibration axis of rotation D 2 at an angle W 2 of less than 180°. In particular, to maintain the desired switching behavior, the angle W 2 is smaller than the angle W 1.

[0047] From the previously described constructive design of the two unbalanced masses 50, 52, it is also evident that when the respective second mass parts 62 and 82 are moved between their first and second end positions, the center of mass of the first unbalanced mass 50 shifts radially, but does not move circumferentially with respect to the first unbalanced mass part 54. In contrast, the center of mass of the second unbalanced mass 52 shifts radially and circumferentially about the second oscillation / vibration axis D2 by an angle of 180°. This means that when the two unbalanced masses 50, 52 are positioned relative to each other as shown in the diagram... Fig. 3 und 4 shown and the respective second unbalance mass parts 62 and 82 are in their respective second end position, i.e., each supported circumferentially on the unbalance mass sections 68 and 88 respectively, as shown in the illustrations of the Fig. 3 und 4 When the unbalanced masses 50, 52 are rotated clockwise, the centers of mass of the two unbalanced masses 50, 52 have an angular offset of 180° to each other, since the center of mass of the first unbalanced mass 50 is essentially above the first oscillation / vibration axis of rotation D 1 and the center of mass of the second unbalanced mass 52 is essentially below the second oscillation / vibration axis of rotation D 2.

[0048] To ensure that the respective unbalance moment of the two unbalance masses 50, 52 is equal, i.e., that the centrifugal forces acting at or represented by the respective centers of mass have the same magnitude, the unbalance mass section 68 of the first unbalance mass section 54 of the first unbalance mass 50 has a larger volume and thus a larger mass than the unbalance mass section 88 of the first unbalance mass section 72 of the second unbalance mass 52. This compensates for the fact that the second unbalance mass section 82 of the second unbalance mass 52 has twice the mass of the second unbalance mass section 62 of the first unbalance mass 50.

[0049] Are the second unbalance mass parts 62 and 82 of the two unbalance masses 50 and 52 supported on the support section 70 and 90 of the first unbalance mass part 54 and 72, respectively, as shown in the illustration of the Fig. 4 In the counterclockwise direction, the center of mass of each of the two unbalanced masses 50, 52 lies above the oscillation / vibration axis D 1 , D 2. Due to the mass distribution present in this state, the center of mass of each of the unbalanced masses 50, 52 has a smaller radial distance to the respective oscillation / vibration axis D 1 , D 2, so that the centrifugal force acting on or represented by the respective center of mass will also be lower during rotation, although the two centrifugal forces acting on the unbalanced masses 50, 52 are in the same direction.

[0050] The following refers to the Fig. 5 und 6 The effect resulting from the switching behavior of the unbalanced masses 50, 50' and 52, 52' of the two oscillation / vibration units 30, 32 of the oscillation / vibration arrangement 28 in the operation of the compactor roller 20 and the soil compactor 10 is described.

[0051] The Fig. 5 Figure 1 shows the compressor roller 20 in oscillation operation of the oscillation / vibration arrangement 28. The two oscillation / vibration units 30, 32 rotate around their respective oscillation / vibration axis D1 and D2, respectively, as shown in the view of the Fig. 5 clockwise and at the same rotational speed. The second unbalance mass sections 62 and 82 of the unbalances 50, 50', 52, 52' are in their respective second end positions, so that the rolling elements 64 and 84, 86 are supported circumferentially by the respective unbalance mass section 68 and 88, respectively, or are carried along by it for circumferential movement. Radially outwards, the rolling elements 64 and 84, 86 are supported by the first guide track 66 and the second guide track 80, respectively. In the Fig. 5 In the depicted rotational state, the center of mass of the first unbalanced masses 50, 50' lies vertically above the first oscillation / vibration axis D1, so that the centrifugal force F1 acting on the first unbalanced masses 50, 50' is directed essentially vertically upwards. For the second unbalanced masses 52, 52', the center of mass lies vertically, or vertically, below the second oscillation / vibration axis D2, so that the centrifugal force F2 acting on the second unbalanced masses 52, 52' is directed essentially vertically downwards. Due to the masses specified for the respective first unbalanced mass parts 54 and 72 on the one hand and the respective second unbalanced mass parts 62 and 82 on the other hand, and thus also the unbalance moments present in the respective first and second unbalanced mass parts 54, 72, 62, 82, the centrifugal forces F 1 , F 2 directed in opposite directions have the same centrifugal force magnitude.This creates a torque acting around the roller's axis of rotation W, which periodically changes direction during the rotation of the two oscillation / vibration units 30, 32, so that the compressor roller 20, or rather its roller shell 24, is periodically accelerated back and forth in the circumferential direction around the roller's axis of rotation W. The compressor roller 20, or rather the oscillation / vibration arrangement 28, thus operates in oscillation mode.

[0052] In Fig. 6 The two oscillation / vibration units 30, 32 are shown in a rotational state in which, compared to the rotational state of the Fig. 5 , the direction of rotation has reversed. The oscillation / vibration units 30 and 32 rotate counterclockwise at the same speed.

[0053] During the transition from the rotational state of the Fig. 5 to the rotational state of the Fig. 6 The second unbalance mass components 62 and 82 move within their respective receiving spaces 60 and 76, respectively, by means of the rolling motion of the rolling elements 64 and 84, 86 along the first guide track 66 and the second guide track 80, respectively, in a circumferential direction relative to the respective first unbalance mass component 54 and 72, respectively, so that they reach their respective first end position. In this state, the second unbalance mass components 62 and 82 are supported circumferentially by the respective support section 70 and 90, respectively, and are carried along by this section for circumferential movement.

[0054] In each of the two unbalanced masses 50, 50', 52, 52', the mass lies in the Fig. 6 The depicted rotational state of the center of mass above the respective oscillation / vibration axis D1, D2, but with a smaller radial distance to it than in the one shown in Fig. 5 The oscillation operation shown. This results in the centrifugal forces F1' and F2' acting on the centers of mass of the unbalanced masses 50, 50', 52, 52' now being directed in the same direction, i.e., they have no phase shift relative to each other, but exhibit a smaller centrifugal force magnitude than in the Fig. 5 The depicted oscillation operation.

[0055] In the Fig. 6 In the depicted rotational state of the oscillation / vibration units 30, 32, the two centrifugal forces F1', F2' add up to a total centrifugal force that is radially directed with respect to the roller's axis of rotation W. The compaction roller 20, or the oscillation / vibration arrangement 28, thus operates in vibratory mode, in which, during rotation of the oscillation / vibration units 30, 32, the resulting total centrifugal force rotates around the roller's axis of rotation W due to the centrifugal forces F1', F2' adding up in each rotational position. This causes the compaction roller 20 to be periodically accelerated upwards and downwards, and correspondingly periodically loads the subgrade 26 to be compacted.

[0056] In the switching between oscillation and vibration operation described above, the mass distribution in the two oscillation / vibration units 30, 32, or the first unbalanced masses 50, 50' and second unbalanced masses 52, 52' respectively, ensures that the centrifugal forces F1, F2 and F1', F2' acting at the respective centers of mass are of the same magnitude. However, in oscillation operation, the centrifugal forces are directed in opposite directions. This is achieved by the unbalanced masses 50, 50', or their respective centers of mass, having a phase shift of approximately 180° relative to the second unbalanced masses 52, 52', or their respective centers of mass. Fig. 6 In the depicted vibration operation, the centrifugal forces F 1 ', F 2 ' acting on the oscillation / vibration units 30, 32 have a lower centrifugal force magnitude, but are directed in the same direction to each other, which is achieved by the fact that, due to the mass distribution in the respective unbalance masses 50, 50', 52, 52', the centers of mass of the two oscillation / vibration units 30, 32 do not have a phase offset to each other.

[0057] To achieve this, not only do the two second unbalance mass components 62, 82 differ from each other in their mass and thus in the unbalance moment they each provide, but the first unbalance mass components 54, 72 also differ from each other in their mass and thus in the unbalance moment they provide. Furthermore, the first unbalance mass component 54 of each first unbalance mass 50, 50' corresponds essentially to the unbalance moment of the respective second unbalance mass components 82 of the second unbalance masses 52, 52' with respect to the unbalance moment they provide. Likewise, the first unbalance mass components 72 of the second unbalance masses 52, 52' correspond essentially to the unbalance moment of the respective second unbalance mass components 62 of the first unbalance masses 50, 50' with respect to the unbalance moment they provide.

[0058] By switching between oscillation and vibration modes with different centrifugal force magnitudes, it is achieved in particular that in vibration mode the periodic movement of the compressor roller 20 is generated with a lower centrifugal force magnitude than in oscillation mode. This makes it possible to operate at a higher rotational speed and thus a higher frequency in vibration mode than in oscillation mode, without excessively increasing the load on the bearings supporting the oscillation / vibration shafts 40, 46. This is further enhanced by the appropriate selection of the masses or mass distributions of the unbalanced mass components 54, 62, and 46.Since the extent of the change in the centrifugal force values ​​during the transition from oscillation operation to vibration operation can be specified in a large range of values ​​by means of the radial positions of the guide tracks 66, 80, the change in rotational speed and thus in frequency with which the compressor roller 20 is periodically loaded can also be freely specified in a large range of values ​​made possible by this switching behavior.

[0059] In conclusion, it should be noted that the setup described above can, of course, be varied in many different aspects without deviating from the functional principle or the basic design principle. For example, the oscillation / vibration units can each have only one or more than two unbalanced masses. The requirement, however, is that each oscillation / vibration unit has the same unbalance moment. The respective secondary unbalanced mass components could also be designed differently. For instance, the secondary rolling elements used in the secondary unbalanced masses could have different dimensions or shapes than the primary rolling elements used in the respective primary unbalanced masses. The different masses of the respective secondary unbalanced mass components can also be achieved, for example, by using essentially identical rolling elements with different masses.For example, the first rolling body to be provided with a lower mass can be designed as a hollow body for the first unbalanced masses, while a second rolling body to be provided for the respective second unbalanced masses can be designed as a solid rolling body and thus provided with a larger mass.

[0060] The structure or mass distribution of the various unbalance masses can also be modified compared to the configuration shown in the figures and described above, insofar as, in the first oscillation / vibration unit 30 or the unbalance masses 50, 50' thereof, the centers of mass M 11 , M 12 of the two unbalance mass parts 54, 62 are located in a different position compared to the configuration shown in the figures. Fig. 3 In the depicted arrangement, the positions of the components relative to the radial line R are interchanged, such that the center of mass M 11 of the first unbalanced mass component 54 lies to the right of the substantially vertical radial line R in the depicted rotational state, and the center of mass M 12 of the second unbalanced mass component 62 lies to the left of the radial line R in both end positions. In this case, the center of mass M 12 of the second unbalanced mass component 62 moves between the two end positions at an angle W 1 greater than 180°.

[0061] Alternatively or additionally, it can be provided that in the second oscillation / vibration unit 32 or the unbalance masses 52, 52' thereof, the centers of mass M 21 , M 22 of the two unbalance mass parts 72, 82 are compared to the one in Fig. 4In the depicted arrangement, the positions of the two unbalanced masses 72 and the masses are interchanged with respect to the radial line R, such that the center of mass M 21 of the first unbalanced mass 72 lies to the left of the substantially vertical radial line R in the depicted rotational state, and the center of mass M 22 of the second unbalanced mass 82 lies to the right of the radial line R in both end positions. In this case, the center of mass M 22 of the second unbalanced mass 82 moves between the two end positions at an angle W 2 greater than 180°.

[0062] If both angles W1, W2 are greater than 180°, the angle W2 is greater than the angle W1 to achieve a suitable switching behavior with regard to the unbalance moments to be set.

[0063] In principle, configurations are also conceivable in which one of the angles W 1 , W 2 is less than 180° and the other is greater than 180° or one of the angles W 1 , W 2 is exactly 180°.

Claims

1. Compactor roller for a soil compactor, comprising a roller shell (24), rotatable about a roller axis of rotation (W) and surrounding a roller interior, an oscillation / vibration assembly (28) arranged in the roller interior (23), wherein the oscillation / vibration assembly (28) comprises: - a first oscillation / vibration unit (30) with at least one first unbalanced mass (50, 50') drivable for rotation about a first oscillation / vibration axis of rotation (D1), wherein the at least one first unbalanced mass (50, 50') comprises a first unbalanced mass part (54) and a second unbalanced mass part (62), movable with respect to the first unbalanced mass part (54) about the first oscillation / vibration axis of rotation (D1) between two end positions, wherein, during rotation of the at least one first unbalanced mass (50, 50') about the first oscillation / vibration axis of rotation (D1) in a first direction of rotation, the second unbalanced mass part (62) of the at least one first unbalanced mass (50, 50') is in its first end position, and during rotation of the at least one first unbalanced mass (50, 50') about the first oscillation / vibration axis of rotation (D1) in a second direction of rotation opposite the first direction of rotation, the second unbalanced mass part (62) of the at least one first unbalanced mass (50, 50') is in its second end position, wherein during movement of the second unbalanced mass part (62) of the at least one first unbalanced mass (50, 50') between its first end position and its second end position, a center of mass (M12) of the second unbalanced mass part (62) of the at least one first unbalanced mass (50, 50') moves about the first oscillation / vibration axis of rotation (D1) in a first predetermined angle (W1), - a second oscillation / vibration unit (32) with at least one second unbalanced mass (52, 52') drivable for rotation about a second oscillation / vibration axis of rotation (D2), wherein the at least one second unbalanced mass (52, 52') comprises a first unbalanced mass part (72) and a second unbalanced mass part (82), movable with respect to the first unbalanced mass part (72) about the second oscillation / vibration axis of rotation (D2) between two end positions, wherein, during rotation of the at least one second unbalanced mass (52, 52') about the second oscillation / vibration axis of rotation (D2) in the first direction of rotation, the second unbalanced mass part (82) of the at least one second unbalanced mass is in its first end position, and during rotation of the at least one second unbalanced mass (52, 52') about the second oscillation / vibration axis of rotation (D2) in the second direction of rotation, the second unbalanced mass part (82) of the at least one second unbalanced mass (52, 52') is in its second end position, wherein during movement of the second unbalanced mass part (82) of the at least one second unbalanced mass (52, 52') between its first end position and its second end position, a center of mass (M22) of the second unbalanced mass part (82) of the at least one second unbalanced mass (52, 52') moves about the second oscillation / vibration axis of rotation (D2) in a second predetermined angle (W2), wherein, for the second unbalanced mass part (62) of the at least one first unbalanced mass (50, 50'), positioned in its first end position, and for the second unbalanced mass part (82) of the at least one second unbalanced mass (52, 52'), positioned in its first end position, a center of mass of the at least one first unbalanced mass (50, 50') and a center of mass of the at least one second unbalanced mass (52, 52') substantial do not have a phase offset to one another, and a first centrifugal force (F1') acting in the center of mass of the at least one first unbalanced mass (50, 50') and a second centrifugal force (F2') acting in the center of mass of the at least one second unbalanced mass (52, 52') are oriented substantially identically to one another and have a substantially identical first centrifugal force value, wherein, for the second unbalanced mass part (62) of the at least one first unbalanced mass (50, 50'), positioned in its second end position, and for the second unbalanced mass part (82) of the at least one second unbalanced mass (52, 52'), positioned in its second end position, the center of mass of the at least one first unbalanced mass (50, 50') and the center of mass of the at least one second unbalanced mass (52, 52') have a phase offset to one another in the range of 180°, and the first centrifugal force (F1) acting in the center of mass of the at least one first unbalanced mass (50, 50') and the second centrifugal force (F2) acting in the center of mass of the at least one second unbalanced mass (52, 52') are oriented substantially opposite to one another and have a substantially identical second centrifugal force value, characterized in that a first guideway (66) with a radially-inwardly oriented guideway surface normal (N1) is provided on the first unbalanced mass part (54) of the at least one first unbalanced mass (50, 50') for moving the second unbalanced mass part (62) of the at least one first unbalanced mass (50, 50'), supported radially outwardly on the first guideway (66), between its first end position and its second end position, and that a second guideway (80) with a radially-inwardly oriented guideway surface normal (N2) is provided on the first unbalanced mass part (72) of the at least one second unbalanced mass (52, 52') for moving the second unbalanced mass part (82) of the at least one first unbalanced mass (52, 52'), supported radially outwardly on the second guideway (80), between its first end position and its second end position.

2. Compactor roller according to claim 1, characterized in that the first predetermined angle (W1) is less than 180° or greater than 180°, and / or that the second predetermined angle (W2) is less than 180° or greater than 180°,3. Compactor roller according to claim 2, characterized in that for the second unbalanced mass part (62) of the at least one first unbalanced mass (50, 50'), positioned in its second end position, the center of mass (M12) of the second unbalanced mass part (62) of the at least one first unbalanced mass (50, 50') and a center of mass (M11) of the first unbalanced mass part (54) of the at least one first unbalanced mass (50, 50') do not lie on a common radial line intersecting the first oscillation / vibration axis of rotation (D1), and / or that for the second unbalanced mass part (82) of the at least one second unbalanced mass (52, 52'), positioned in its second end position, the center of mass (M22) of the second unbalanced mass part (82) of the at least one second unbalanced mass (52, 52'), and a center of mass (M21) of the first unbalanced mass part (72) of the at least one second unbalanced mass (52, 52') do not lie on a common radial line intersecting the second oscillation / vibration axis of rotation (D2).

4. Compactor roller according to claim 3, characterized in that for the second unbalanced mass part (62) of the at least one first unbalanced mass (50, 50'), positioned in its first end position, and for the second unbalanced mass part (62) of the at least one first unbalanced mass (50, 50'), positioned in its second end position, the center of mass (M12) of the second unbalanced mass part (62) of the at least one first unbalanced mass (50, 50') and the center of mass (M11) of the first unbalanced mass part (54) of the at least one first unbalanced mass (50, 50') lie in the circumferential direction on both sides of a common radial line (R) intersecting the first oscillation / vibration axis of rotation (D1), and / or that for the second unbalanced mass part (82) of the at least one second unbalanced mass (52, 52'), positioned in its first end position, and for the second unbalanced mass part (82) of the at least one second unbalanced mass (52, 52'), positioned in its second end position, the center of mass (M22) of the second unbalanced mass part (82) of the at least one second unbalanced mass (52, 52'), and the center of mass (M21) of the first unbalanced mass part (72) of the at least one second unbalanced mass (52, 52') lie in the circumferential direction on both sides of a common radial line (R) intersecting the second oscillation / vibration axis of rotation (D2).

5. Compactor roller according to one of the preceding claims, characterized in that when the first predetermined angle (W1) and the second predetermined angle (W2) are less than 180°, then the first predetermined angle (W1) is greater than the second predetermined angle (W2), and when the first predetermined (W1) and the second predetermined (W2) are greater than 180°, then the first predetermined angle (W1) is smaller than the second predetermined angle (W2).

6. Compactor roller according to one of the preceding claims, characterized in that the first guideway (66) extends only over a partial circumferential area about the first oscillation / vibration axis of rotation (D1) and that the second guideway (80) extends only over a partial circumferential area about the second oscillation / vibration axis of rotation (D2), or / and in that a radial distance of the first guideway (66) to the first oscillation / vibration axis of rotation (D1) substantially corresponds to a radial distance of the second guideway (80) to the second oscillation / vibration axis of rotation (D2).

7. Compactor roller according to one of the preceding claims, characterized in that the second unbalanced mass part (62) of the at least one first unbalanced mass (50, 50') comprises at least one first rolling body (64), rolling along the first guideway (60) during movement between the first end position and the second end position, and that the second unbalanced mass part of the at least one second unbalanced mass (52, 52') comprises at least one second rolling body (84, 86), rolling along the second guideway (80) during movement between the first end position and the second end position, preferably wherein the number of first rolling bodies (64) differs from the number of second rolling bodies (84, 86).

8. Compactor roller according to claim 7, characterized in that all first rolling bodies (64) and all second rolling bodies (84, 86) are designed identically to one another, or in that at least one first rolling body (64) differs from at least one second rolling body (84, 86).

9. Compactor roller according to one of the preceding claims, characterized in that the first oscillation / vibration axis of rotation (D1) and the second oscillation / vibration axis of rotation (D2) are arranged substantially parallel to one another and to the roller axis of rotation (W), and / or that the first oscillation / vibration axis of rotation (D1) and the second oscillation / vibration axis of rotation (D2) have an angular distance of approximately 180° with respect to the roller axis of rotation (W).

10. Compactor roller according to one of the preceding claims, characterized in that the first unbalanced mass part (54) of the at least one first unbalanced mass (50, 50') is supported on a first oscillation / vibration shaft (40), rotatably drivable about the first oscillation / vibration axis of rotation (D1), and / or the first oscillation / vibration shaft (40) provides at least one part of the first unbalanced mass part (54) of the at least one first unbalanced mass (50, 50'), and that the first unbalanced mass part (72) of the at least one second unbalanced mass (52, 52') is supported on a second oscillation / vibration shaft (46), rotatably drivable about the second oscillation / vibration axis of rotation (D2), and / or the second oscillation / vibration shaft (46) provides at least one part of the first unbalanced mass part (72) of the at least one second unbalanced mass (52, 52'),11. Compactor roller according to one of the preceding claims, characterized in that the oscillation / vibration assembly (28) comprises an oscillation / vibration drive (34), and that the at least one first unbalanced mass (50, 50') of the first oscillation / vibration unit (30) and the at least one second unbalanced mass (52, 52') of the second oscillation / vibration unit (32) are drivable by the oscillation / vibration drive (34) to rotate in the same direction of rotation and at the same rotational speed.

12. Compactor roller according to one of the preceding claims, characterized in that the first oscillation / vibration unit (30) comprises two first unbalanced masses (50, 50'), arranged spaced apart from one another in the direction of the first oscillation / vibration axis of rotation (D1) and preferably designed identically to one another, and / or that the second oscillation / vibration unit (32) comprises two second unbalanced masses (52, 52'), arranged spaced apart from one another in the direction of the second oscillation / vibration axis of rotation (D2) and preferably designed identically to one another, preferably wherein the second centrifugal force value is greater than the first centrifugal force value.

13. Compactor roller according to one of the preceding claims, characterized in that an unbalanced torque of the first unbalanced mass part (54) of the at least one first unbalanced mass (50, 50') substantially corresponds to an unbalanced torque of the second unbalanced mass part (82) of the at least one second unbalanced mass (52, 52'), and that an unbalanced torque of the first unbalanced mass part (72) of the at least one second unbalanced mass (52, 52') substantially corresponds to an unbalanced torque of the second unbalanced mass part (62) of the at least one first unbalanced mass (50, 50'), wherein each unbalanced torque is defined as: U = m × r , where: U is the unbalanced torque of a respective unbalanced mass part (54, 62, 72, 82), m is an inertial mass of the unbalanced mass part (54, 62, 72, 82) acting in the center of mass (M11, M12, M21, M22) of a respective unbalanced mass part, and r is a radial distance of the center of mass (M11, M12, M21, M22) of a respective unbalanced mass part (54, 62, 72, 82) to the assigned oscillation / vibration axis of rotation (D1, D2).

14. Compactor roller according to claim 13, characterized in that the first unbalanced mass part (54) of the at least one first unbalanced mass (50, 50') has a greater unbalanced torque than the first unbalanced mass part (72) of the at least one second unbalanced mass (52, 52'), and that the second unbalanced mass part (62) of the at least one first unbalanced mass (50, 50') has a smaller unbalanced torque that the second unbalanced mass part of the at least one second unbalanced mass (52, 52').

15. Soil compactor, comprising at least one compactor roller (20) according to one of the preceding claims.