Unbalance exciter for a soil compacting machine, rolling bandage and soil compacting machine

Abstract

The invention relates to an unbalance exciter for a soil compaction machine, a roller drum and a soil compaction machine.

Description

[0001] The invention relates to an unbalance exciter for a soil compaction machine, a roller drum and a soil compaction machine.

[0002] Soil compaction machines, such as rollers and vibratory plates, often incorporate a vibration excitation device in the form of an unbalanced exciter to actively impart vibrations to a soil contact element, such as a roller drum or a base plate, thereby initiating a dynamic compaction process. Such unbalanced exciters may have a drive shaft rotating around an axis of rotation, on which an unbalanced mass is mounted eccentrically to this axis and carried along by the drive shaft during rotation. The drive shaft is typically supported in bearings of a supporting structure.With such unbalance exciters, considerable bending forces can occur on the drive shaft due to the unbalance mass that is continuously carried along during rotation. This not only necessitates a comparatively robust design of the drive shaft but can also lead to relatively high bearing loads. In particular, the bearings of the drive shaft of such unbalance exciters are therefore regularly subject to increased wear.

[0003] DE1041283B discloses an unbalance exciter with four spherical rolling elements and eccentrically arranged raceways. Although the bending force load on the drive shaft could be reduced in this embodiment, comparatively high frictional forces occur between the rolling elements and the drivers supported by the drive shaft. DE1691830U discloses an unbalance exciter with two spherical or cylindrical rolling elements and drivers supported by the drive shaft. The raceway of the rolling elements is also eccentric to the axis of rotation of the drive shaft. These two arrangements have in common that the bearing of the rolling elements is undefined and they can, for example, flip over when the drive shaft is switched off. Moreover, the driver of DE1691830U itself can contribute significantly to the unbalance, which can lead to deflection of the drive shaft.DE1198555B relates to a device for driving or pulling piles with two cylindrical rolling elements which are guided coaxially to each other in an eccentrically or ovally extending raceway. The vibratory device according to DE2706667A1 discloses the use of several unbalanced elements rolling on a raceway that is at least partially elliptical and radially displaceable.

[0004] The object of the invention is to provide an improved unbalance exciter compared to known unbalance exciters, in which, in particular, the radial bearing loads occurring in the rotary bearings of the drive shaft are comparatively low.

[0005] The problem is solved using an unbalanced exciter, a roller drum, and a soil compaction machine according to the independent claims. Preferred embodiments are specified in the dependent claims.

[0006] In a first aspect, the problem is solved by an unbalance exciter according to the invention, in particular an unbalance exciter for a soil compaction machine. The unbalance exciter comprises a support structure and a drive shaft rotatable about a vibration excitation rotation axis relative to the support structure. The support structure can, in particular, be a housing-like support structure on which the drive shaft of the unbalance exciter is rotatably mounted. This support structure can be designed as a housing-like support structure that is largely closed off from the outside environment. The support structure can thus, in particular, be designed as a support frame or frame-like basic structure of the unbalance exciter. The vibration excitation rotation axis is the axis about which the drive shaft of the unbalance exciter rotates relative to the support structure during rotation or vibration excitation operation of the unbalance exciter.The drive shaft can be mounted on the support structure using suitable bearings, in particular rotary bearings, especially rolling bearings.

[0007] The unbalance exciter according to the invention further comprises a drive unit that rotates with the drive shaft around the axis of rotation of the vibration excitation. The purpose of the drive unit is to carry one or more of the unbalance mass elements, described in more detail below, along with the drive shaft during rotation around the axis of rotation of the vibration excitation, and in particular to drag them along in the direction of rotation of the drive shaft. For this purpose, it can be provided that the drive unit is fixedly connected to the drive shaft. This can be achieved via one or more detachable or permanent connections, such as screw and / or welded connections. It is also possible that the drive shaft and the drive unit are formed in one piece and / or of a single material, for example, from a single casting.The drive element can, in particular, extend radially outwards from the drive shaft, which preferably runs along the axis of rotation of the vibration excitation or at least parallel to it. It is thus possible for the drive element itself to form an eccentric mass in conjunction with the drive shaft. However, it is preferred if this eccentricity potentially generated by the drive element is significantly smaller than the eccentricity formed by the unbalanced mass(s) described in more detail below. It is also possible, however, for the entire assembly of drive shaft and drive element to be designed such that it does not, on its own, form an eccentricity during rotation about the axis of rotation of the vibration excitation, or that the center of mass of this assembly lies on the axis of rotation of the vibration excitation.Ideally, the entire assembly, consisting of the drive shaft and drive mechanism, should be balanced or rotationally neutral with respect to the axis of vibration excitation. Specifically, the drive mechanism can be designed, for example, as a radially extending bearing arm or as a bearing fork with two or more radially extending bearing arms.

[0008] The unbalance exciter includes at least one unbalance mass element, which is rotatable relative to the drive unit and thus also relative to the drive shaft about a rolling axis, in particular one running parallel to the vibration excitation axis. The unbalance mass element is connected to the drive unit via a bearing assembly, so that the drive unit rotates together with the unbalance mass element about the vibration excitation axis. The unbalance mass element is therefore a mass unit whose center of mass is radially offset from the vibration excitation axis. It is provided that the unbalance mass element is not statically fixed directly to the drive unit, but rather connected via the bearing assembly. The bearing assembly can, in particular, be designed as a rotary bearing.The bearing arrangement ensures that the unbalanced mass element is movable around the rolling rotation axis, i.e., at least and in particular exclusively with one degree of freedom, relative to the drive mechanism and thus also relative to the drive shaft. Simultaneously, the drive mechanism guides or carries the unbalanced mass element during a rotational movement around the vibration excitation rotation axis, so that it, together with the drive mechanism, is also rotatable around the vibration excitation rotation axis.

[0009] The unbalance exciter according to the invention further comprises a support surface extending, at least substantially, circularly around the vibration excitation rotation axis and, in particular, being fixed in position relative to the supporting structure. The unbalance mass element rests against this support surface in the radial direction to the vibration excitation rotation axis, or can rest against it during rotation of the drive shaft. During rotation of the drive shaft, the unbalance mass element rolls around the vibration excitation rotation axis and rotates around the rolling rotation axis. The support surface thus surrounds the unbalance mass element and its circular path in the radial direction, so that the centrifugal forces emanating from the unbalance mass element rotating around the vibration excitation rotation axis during rotation press the unbalance mass element radially outwards onto the support surface and, in particular, do not pull on the drive shaft and / or the drive mechanism.The support surface thus represents a rolling path for the unbalanced mass element, extending, at least essentially, in a circle around the axis of rotation of the vibration excitation. During rotational operation of the unbalanced mass generator, the unbalanced mass element rolls along the rolling path around the axis of rotation, while simultaneously rotating as a whole around the axis of rotation of the vibration excitation due to its connection via the bearing assembly to the drive unit. This rotation generates, for example, the desired vibration for dynamic soil compaction in the compaction process mentioned earlier. The rotational operation of the unbalanced mass generator is therefore characterized, in particular, by the fact that during this operation, the drive shaft, and with it the drive unit and the unbalanced mass element, rotate around the axis of rotation of the vibration excitation, while the unbalanced mass element simultaneously rotates around the axis of rotation of the vibration excitation.Relative to the supporting structure, the overall movement of at least one unbalanced mass element thus consists of a superposition of these two individual rotational movements.

[0010] In order to ensure, for example to compensate for manufacturing tolerances and / or due to wear occurring during operation of the unbalance exciter, a reliable and, as far as possible, continuous contact of the unbalance mass element with the support surface over the entire rotational movement of the unbalance mass element, both around itself, i.e., around the rolling rotation axis, and with the entire assembly of drive shaft and drive device around the vibration excitation rotation axis, the invention finally provides that the bearing device between the drive device and the unbalance mass unit or...The unbalanced mass element comprises an eccentric bearing assembly with an eccentric axis of rotation, designed such that the radial distance between the rolling rotation axis and the vibration excitation rotation axis is adjustable within a range defined by the eccentric bearing assembly, in particular an eccentric bearing, especially to compensate for tolerances. With the aid of the eccentric bearing, the radial distance of the rolling rotation axis, and thus, for example, also the radial distance of a contact area of ​​the unbalanced mass element located radially outside the vibration excitation rotation axis to the support surface, can be changed or adjusted by an outward and / or inward rotation movement, and specifically not by a linear adjustment movement in the radial direction. It may be provided that the adjustment range is defined exclusively by the eccentric bearing assembly.However, it is also possible that additional means, such as one or more stops, are present to define the limits of the adjustment range. These stop stops, in conjunction with the eccentric bearing assembly, define the adjustment range. This adjustment movement is driven radially outwards towards the vibration excitation axis by centrifugal forces acting on the unbalanced mass. In the radial inwards direction, the adjustment movement is achieved by the support surface pressing the unbalanced mass element towards the vibration excitation axis. Although the maximum extent of the adjustment movement radially outwards towards the vibration excitation axis is theoretically limited by the design of the eccentric bearing assembly, this is preferably limited by the support surface, thus ensuring that the unbalanced mass element is always in contact with the support surface during vibration excitation rotation.In the radial direction inwards, i.e. in the direction of the vibration rotation axis, the maximum extent of the adjustment movement can be formed by the eccentric bearing device itself.

[0011] The inventive design of the unbalance exciter described above ensures not only that the support of the unbalance mass no longer occurs on the drive shaft and / or the drive unit, but on the support structure, which is designed, for example, as a housing. This allows the required bending stiffness of the drive shaft to be significantly reduced, since the centrifugal force load occurring on the drive shaft during vibration excitation rotation is significantly reduced or even eliminated.At the same time, only with the help of the eccentric bearing device is it sufficiently ensured that the continuous contact of the unbalance mass element with the support surface desired for support can be reliably and with low friction compensated for naturally occurring manufacturing tolerances and / or tolerances that develop due to wear and / or operation in the radial distance of the support surface and / or the outer contact area of ​​the unbalance mass element relative to the vibration excitation rotation axis.

[0012] It can be provided that the vibration excitation rotation axis, the rolling rotation axis, and the eccentric rotation axis are parallel to each other, and it is particularly preferred if both the rolling rotation axis and the eccentric rotation axis are radially spaced from the vibration excitation rotation axis. Ideally, the radial distance of the eccentric rotation axis to the vibration excitation rotation axis is constant or fixed, and the radial distance of the rolling rotation axis to the vibration excitation rotation axis is variable within a range by adjusting the eccentric bearing assembly about the eccentric rotation axis, wherein the magnitude of the radial distance of the eccentric rotation axis to the vibration excitation rotation axis ideally lies within the range of that radial distance within which the magnitude of the radial distance of the rolling rotation axis to the vibration excitation rotation axis is variable.Additionally or alternatively, it is preferred if the radial distance of the eccentric axis of rotation to the rolling axis of rotation, which is particularly precisely defined, is smaller than the radial distance of the eccentric axis of rotation to the vibration excitation axis of rotation, in particular at most one-fifth as large, and most especially at most one-tenth as large. These two distances can be considered as lifting arm lengths, which can preferably be designed with respect to their length in the specified dimensions.

[0013] The eccentric bearing assembly can be designed in various ways. The use of a cam track or other alternative designs is also possible. Preferably, however, the eccentric bearing assembly is designed as an eccentric rotary bearing assembly. The eccentricity is thus preferably adjusted by a rotary movement. Although various suitable rotary bearing types, such as rolling bearings or ball bearings, can be used for the specific design of the eccentric bearing assembly, it is advantageous if the eccentric bearing assembly is a radial plain bearing or is designed as such. A plain bearing is characterized, in particular, by the fact that a rotating part slides along a non-rotating part.Additional friction-reducing measures can be taken to specifically design this plain bearing. For example, the plain bearing can be made of low-friction materials, include a lubricating film, and / or incorporate one or more plastic bearing bushings and / or sleeves, such as those made of polyfluorotetraethylene, and / or have one or more friction-reducing coatings in the bearing area. The eccentric bearing assembly can be designed as a thrust bearing or as a radial-thrust bearing. Ideally, the eccentric bearing assembly should be designed to allow only a single degree of freedom, specifically a rotational movement around the eccentric axis.

[0014] The eccentric bearing assembly can be designed to allow a complete rotation around the eccentric axis of rotation. However, it can also be designed to restrict rotation to a defined angular range, for example, <180°, particularly <160°, for which one or more rotation stops or similar devices may be provided.

[0015] The design of the bearing(s) that allow the drive shaft to rotate relative to the support structure about the vibration excitation axis and / or the unbalanced mass element to rotate relative to the drive shaft and / or the drive unit about the rolling rotation axis can also vary. However, due to the rotational movements occurring around the respective axes during vibration excitation operation, it is preferred for these bearings to be designed as rolling bearings, particularly deep groove ball bearings.

[0016] Further advantageous embodiments of the invention may relate to the specific design of the bearing assembly in which the unbalanced mass element is rotatably mounted about the rolling axis. For example, this bearing assembly may comprise a bearing axis element extending longitudinally in the direction of the rolling axis, and at least one eccentric disk of the eccentric bearing assembly may be rotationally fixed to the bearing axis element. The eccentric disk is an element, particularly a disk-shaped one, that comprises a circular radial rim. The center point of the circular rim, particularly in a projection of the eccentric disk onto a virtual projection plane extending radially to the rolling axis and / or eccentric axis of rotation, ideally lies on the eccentric axis of rotation and adjacent to the rolling axis of rotation.The edge of the eccentric disc can be cylindrical, convex, or concave, and may include one or more annular grooves or be similarly shaped. In particular, it may be provided that two stub axles extending towards the rolling rotation axis on both end faces of the eccentric disc are present. Alternatively, a bearing axis element may be present, with an eccentric disc formed at each of its opposite ends, wherein the two eccentric discs are specifically designed and arranged to be congruent in the axial direction of the bearing axis element or in the axial direction of the eccentric rotation axis. The unbalance mass element may be rotatably mounted on the bearing axis element(s), in particular such that the rolling rotation axis is coaxial with the longitudinal axis of the bearing axis element(s).Alternatively, it is also possible, for example, that the bearing axle element, particularly together with the unbalance mass element, is rotatably mounted in the eccentric disc(s). In particular, it is also possible that the bearing axle element is rotationally fixed to the unbalance mass element and rotates together with it around the rolling axis in the eccentric disc via a rotary bearing.

[0017] Several particularly advantageous design options exist regarding the specific configuration of the drive mechanism. For example, the drive mechanism can be designed as a drive fork with two bearing projections spaced apart axially along the axis of vibration excitation and projecting radially. In this variant, the unbalanced mass element can be mounted between the two bearing projections in the axial direction of the axis of vibration excitation. A bearing projection thus extends to each end face of the unbalanced mass element in the rolling direction. Alternatively, the drive mechanism can also be designed as a drive tongue or web with a bearing projection spaced apart axially along the axis of vibration excitation and projecting radially.In this case, the unbalance mass element can have two partial unbalance mass elements positioned one behind the other in the axial direction of the vibration excitation rotation axis, which are mounted on opposite sides of the bearing projection. Viewed in the axial direction of the rolling rotation axis, one of the two partial unbalance mass elements is then located in front of and one after the bearing projection.

[0018] Further advantageous variations of the invention may relate to the design of the unbalanced mass element itself. For example, it may be preferred if it has an overall convex shape, in particular, for instance, an at least partially cylindrical outer circumferential surface or a cylindrical outer shell surface, i.e., the shape of a right circular cylinder. In this way, at least a linear contact area with the support surface can be obtained relatively easily, thereby preventing the contact forces transmitted from the unbalanced mass element to the support surface from concentrating at a single point.

[0019] There are also variations in the design of the support surface. The support surface forms the track or counter-surface for the unbalanced mass element rolling on it. The support surface is therefore preferably designed such that it is, at least partially, complementary to the radially outer path of the unbalanced mass element, which rotates about both the vibration excitation axis and the rolling axis during vibration excitation operation. Particularly if the unbalanced mass element thus comprises, for example, a cylindrical outer shell, it may be preferable for the support surface to be entirely hollow-cylindrical, especially in the form of a hollow, and particularly straight, circular hollow cylinder.Additionally or alternatively, the support surface can also have a coating and / or one or more hardened bearing rings to enable smoother running and reduced wear. These can be pressed into the supporting structure or, if the supporting structure is also formed by a housing, into the housing and / or bonded in place or attached in another suitable manner.

[0020] The unbalanced mass element is rotatable around the rolling rotation axis via the bearing assembly relative to the drive assembly and relative to the drive shaft, as mentioned above. Ideally, the unbalanced mass element can therefore be designed such that, viewed from the drive shaft, it extends completely onto one side of the drive shaft. In a sectional view along the vibration excitation rotation axis and in a relative position where the rolling rotation axis also lies in this sectional plane, the unbalanced mass element is thus ideally located entirely on one side of the drive shaft, adjacent to the drive shaft. However, it can be advantageous to design the unbalanced mass element to be relatively large, particularly with regard to the radius or diameter of the unbalanced mass element around the rolling rotation axis, in order to minimize the rolling or...The rotational speed of the unbalanced mass element as it rolls on the support surface is to be kept as low as possible. In a particularly preferred embodiment, it is therefore provided that the maximum radial outer diameter of the unbalanced mass element, or the diameter of the unbalanced mass element in the radial direction to the rolling rotation axis, is greater than half the maximum inner diameter of the circular support surface, or the diameter of the circular support surface in the radial direction to the vibration excitation rotation axis. These ratios refer to a region of the unbalanced mass element and the support surface in a common cross-sectional plane perpendicular to the vibration excitation rotation axis and / or rolling rotation axis. In this case, the unbalanced mass element thus projects beyond or intersects the vibration excitation rotation axis in the common cross-sectional plane.This is one of the ways in which a comparatively compact imbalance agent can be provided.

[0021] It may be additionally or alternatively preferred, particularly if the maximum outer diameter of the unbalanced mass element is greater than half the maximum inner diameter of the circular support surface, for the drive shaft to have a recess extending radially and axially along the axis of rotation of the vibration excitation for at least partial reception of the unbalanced mass. The recess refers in particular to a region in which, extending axially parallel to the axis of rotation of the vibration excitation of the adjacent region of the drive shaft, there is at least temporarily no material of the drive shaft. This region may be at least partially filled by at least parts of the drive mechanism and / or the unbalanced mass. This recess may be designed such that it extends at least partially along the axial path of the axis of rotation of the vibration excitation.The recess can also extend radially to the vibration excitation rotation axis on one side. Additionally or alternatively, it can be provided that the drive element projects from the drive shaft towards the recess and / or extends through the recess from the drive shaft. It can be provided that the dimensions of the recess are not only selected to create sufficient space for, for example, the unbalanced mass element and / or parts of the drive element, particularly those overlapping the vibration excitation rotation axis as described above, but also to ensure that the drive shaft and drive element are balanced as a whole with respect to the vibration excitation rotation axis.In other words, the recess can also be dimensioned so that the center of mass of the entire assembly, consisting of the drive shaft and drive mechanism, lies on the vibration excitation axis of rotation. In this way, loads acting radially along the vibration excitation axis on one or more of the rotary bearings supporting the drive shaft can be minimized, and ideally completely eliminated, during vibration excitation operation. These improvements can also contribute to a particularly compact design of the unbalance exciter.

[0022] It may be provided that the area of ​​the support surface and the space occupied by the drive shaft, including the drive mechanism and the unbalanced mass element, during vibration excitation operation is encapsulated from the external environment of the unbalanced exciter, in order to effectively protect it, for example, from the ingress of foreign objects. For this purpose, the unbalanced exciter can comprise a housing that surrounds this area. It is particularly preferred if the unbalanced exciter comprises a housing that forms the support structure or a housing formed by the support structure. In this case, the housing and support structure have a dual function: specifically, the protection of the aforementioned interior space and the support function for the rotating components, in particular the support function for the unbalanced mass element and the drive shaft, which roll on the support surface during vibration excitation rotation operation.

[0023] The housing allows the unbalance exciter to be designed as a relatively compact and easily installed module. The housing can therefore preferably also include a bearing flange for attaching the unbalance exciter to a higher-level bearing structure. Such a higher-level bearing structure could be, for example, a base plate of a vibratory plate compactor or a roller drum, in particular a disc of a roller drum. In this way, the unbalance exciter can be directly connected to a support structure of a soil contact device of a soil compaction machine. Additionally or alternatively, the housing can comprise a cover element and a cup element, wherein a slewing bearing, particularly in the form of a rolling bearing, is preferably provided in the base of both the cover element and the cup element.Two cover elements and / or housing halves, axially spaced apart and opposing each other in the axial direction of the vibration excitation rotation axis, can also be provided. Additionally or alternatively, it is also possible for the housing to have an interior space, which, as mentioned above, is particularly encapsulated or sealed from the external environment, and whose wall surface at least partially forms the support surface. This, too, can contribute to a comparatively compact design of the unbalance exciter.

[0024] The specific drive mechanism for the drive shaft can vary and may, for example, be a suitable drive motor, such as a hydraulic motor, a drive gearbox, and / or similar device. However, an embodiment in which the drive shaft is directly connected to an electric motor and / or, in particular, is rotationally fixed to the rotor of an electric motor is especially suitable. Thus, an electric direct drive can even be used, which is primarily due to the fact that, thanks to the arrangement according to the invention, bending forces occurring on the drive shaft during vibration excitation rotation, for example, due to centrifugal forces acting directly on the drive shaft, can be practically eliminated, and the entire assembly of drive shaft and drive unit can therefore be balanced almost perfectly with respect to the vibration excitation rotation axis.This can also, either as a supplement or on its own, enable the comparatively compact design of the unbalance exciter, even including the drive motor, especially as a cohesive and manageable module. The drive shaft can also be designed as a single component with the rotor of an electric motor. If the drive shaft is designed as a separate component from the rotor, the connection between these two elements can be achieved via a damping element, for example, a suitable coupling, such as an elastomer coupling. Additionally or alternatively, vibration-damped mounting of the electric motor itself relative to its supporting structure can also be provided.

[0025] A further aspect of the invention relates to a roller bandage with a substantially hollow cylindrical bandage shell and with at least one, in particular several, unbalance exciters arranged in the interior of the bandage shell. The individual unbalance exciters can be designed, in particular, as described above. One or more of the unbalance exciters can thus each comprise a support structure, a drive shaft rotatable about a vibration excitation rotation axis relative to the support structure, a drive element, in particular fixedly connected to the drive shaft and rotating with the drive shaft about the vibration excitation rotation axis, and an unbalance mass element that is rotatable about a rolling rotation axis, in particular parallel to the vibration excitation rotation axis, relative to the drive element.The respective unbalanced mass element can be connected to the respective drive unit via a bearing assembly, so that the drive unit rotates together with the unbalanced mass element around the respective rolling rotation axis around the vibration excitation rotation axis. Furthermore, each of the unbalanced mass exciters can be provided with a support surface extending circularly around the vibration excitation rotation axis, and in particular, fixed to the supporting structure. The respective unbalanced mass element rests on this support surface radially outwards to the vibration excitation rotation axis, and the unbalanced mass element rolls on this surface during rotation of the drive shaft around the vibration excitation rotation axis, thereby rotating around the rolling rotation axis.With regard to individual preferred further development possibilities of the individual features of the unbalance exciter(s) mentioned in relation to this aspect of the invention, reference is made to the preceding explanations concerning the unbalance exciter according to the invention.

[0026] In particular, the imbalance exciter can be designed in a manner corresponding to the imbalance exciter according to the invention.

[0027] It can be provided that the rolling drum comprises two or more of the unbalance exciters, in particular two or more identical unbalance exciters, and most especially two or more of the unbalance exciters according to the invention. These two or more unbalance exciters can be arranged in the interior of the rolling drum such that the vibration excitation rotation axes of the at least two unbalance exciters run parallel to each other, and in particular the vibration excitation rotation axes of all unbalance exciters encompassed by the rolling drum run parallel to each other. The two or more unbalance exciters can be driven by a common drive motor or by individual drive motors, in particular electric motors.

[0028] Due to the potentially compact design of the unbalance exciters according to the invention, it is possible and also preferred if the rolling drum, in particular precisely and exclusively, has four unbalance exciters. These can, for example, be arranged in pairs on two different planes, in particular such that the vibration excitation rotation axes of one pair of unbalance exciters on one plane are coaxial with the vibration excitation rotation axes of one pair of unbalance exciters on the other plane. It can also be provided that the multiple, in particular four, unbalance exciters are arranged on or in a common plane. This means that the four unbalance exciters are arranged at the same level when viewed in the direction of a rolling axis of the rolling drum, in particular at least with regard to their support surfaces and / or unbalance mass elements.Ideally, the four vibration exciters are connected to a drum of the rolling drum via a common support structure, for example, by means of a common disc. Alternatively, the rolling drum may have two or more discs, each supporting two or more vibration exciters. Regardless of the specific spatial configuration of the one or more discs, each supporting two or more vibration exciters, these exciters are preferably arranged at least in pairs at the same height in a common virtual reference plane perpendicular to the vibration excitation rotation axis and in the axial direction of the vibration excitation rotation axis.

[0029] Another aspect of the invention relates to a soil compaction machine with one or more vibratory exciters and / or one or more roller drums according to the invention. The soil compaction machine can be, in particular, a vibratory plate compactor or a roller, especially a self-propelled one, such as a hand-operated roller, a trench roller, especially a remote-controlled one, a tandem roller, or a roller train. Particularly for the tandem roller and the roller train, it can be provided that these include a driver's platform from which the soil compaction machine is operated.

[0030] A preferred further development of the soil compaction machine comprises a control unit designed to control the direction of rotation and / or the rotational frequency of the drive shafts of the vibratory exciter, in particular the at least two vibratory exciters and especially the at least four vibratory exciters, about their respective vibration excitation rotation axis, particularly individually. In this way, a wide variety of vibration patterns can be obtained by using two or more vibratory exciters, such as operating the existing vibratory exciters together as a circular exciter, directional vibrator, etc. Furthermore, by integrating the vibratory unit into a roller drum, an oscillating drum can be obtained, for example. Vibratory plates can be operated in a forward-moving and / or reversible manner, or can be steered by means of the vibratory exciter control.

[0031] The invention is explained in more detail below with reference to the exemplary embodiments shown in the figures, in particular building upon the preceding explanations. The figures schematically show: Fig. 1: A side view of a soil compaction machine of the type articulated tandem roller; Fig. 2: A side view of a soil compaction machine of the type roller train; Fig. 3: A side view of a soil compaction machine of the type articulated tandem roller; Fig. 4: A side view of a soil compaction machine of the type trench roller; Fig. 5: A side view of a soil compaction machine of the type vibratory plate; Fig. 6: A perspective sectional view through a first embodiment of an unbalance exciter; Fig. 7: A detail view of the first embodiment at minimum radial distance; Fig. 8: The detail view from Fig. 7 at maximum radial spacing; Fig. 9, the detailed view from Fig. 6with flanged drive motor; Fig. 10 a cross-sectional view of the first embodiment with medium radial spacing; Fig. 11 a cross-sectional view of a second embodiment of an unbalance exciter; Fig. 12 a perspective sectional view through a third embodiment of an unbalance exciter without a cover bell; Fig. 13 a perspective sectional view through the third embodiment of an unbalance exciter with a cover bell; Fig. 14 a cross-sectional view of the third embodiment with medium radial spacing; Fig. 15 a side view of a fourth embodiment of an unbalance exciter with small radial spacing; Fig. 16 a side view of the fourth embodiment with medium radial spacing; Fig. 17 a side view of the fourth embodiment with large radial spacing; Fig. 18 a side view of a rolling band with several unbalance exciters; Fig. 19 a cross-sectional view of the rolling band made of Fig. 18Fig. 20 shows a side view of a rolling drum with several unbalance exciters; and Fig. 21 shows a cross-sectional view of the rolling drum made of Fig. 20 .

[0032] Identical or similarly functioning components are designated with the same reference numerals in the figures. Repeating components are not necessarily designated separately in each figure.

[0033] The Figures 1 to 5 The figures show various soil compaction machines, each in a side view.

[0034] Together we can achieve in the Figures 1 to 5 The soil compaction machines 1 shown may have a machine frame 2, a drive unit 3, a ground contact device 4 and / or one or more vibratory exciters 5. Specifically, the soil compaction machine 1 is as follows: Fig. 1 around a articulated tandem roller, according to Fig. 2 to use a roller train, according to Fig. 3 around an articulated tandem roller, according to Fig. 4to use a trench roller and according to Fig. 5 around a vibratory plate compactor. The machine frame 2 can, in particular, be a supporting structure of the soil compaction machine 1, which, for example, supports or mounts the drive unit 3, the ground contact device 4 and / or a driver's platform 6, etc. The soil compaction machines 1 can also be controlled by means of a remote control, as, for example, in the case of the soil compaction machine 1 according to Fig. 4 , or for hand-operated operation, as for example in the case of the soil compaction machine 1 according to Fig. 5The soil compaction machine 1 may be designed to be self-propelled or move independently over the ground. A drive unit 3 may also be part of the soil compaction machine 1. This drive unit 3 may be designed to drive one or more drive motors and / or one or more vibratory exciters 5. In addition to a drive motor, for example, an internal combustion and / or electric motor, the drive unit 3 may comprise one or more drive trains, in particular mechanical and / or hydraulic and / or electrical. Direct drive of one or more vibratory exciters 5 and / or one or more drive units 7 by means of a drive motor, in particular an electric or hydraulic motor, is also possible.The driving devices 7 can be, for example, wheels and / or the ground contact devices 4, in particular roller drums, as in the embodiments in the . Figures 1 to 4 shown.

[0035] The unbalance exciter(s) 5 can be used to subject the ground contact device 4 to vibrations during compaction operation of the soil compaction machine 1, thereby enabling dynamic compaction operation. Additionally, the vibrations generated by the unbalance exciter(s) 5 can also be used for driving the machine in a working / movement direction A and / or for steering movements of the soil compaction machine 1, as is particularly relevant in the case of the Fig. 5 The illustrated soil compaction machine 1 in the form of a vibrating plate may be the case.

[0036] In the Figures 6 to 19Various possibilities for the construction and different operating modes of such an unbalance exciter 5 are explained in more detail using various exemplary embodiments.

[0037] A first possible embodiment of an imbalance exciter 5 is in the Fig. 6 This is shown using a perspective sectional view. The section plane runs along a vibration excitation rotation axis 8 through the unbalance exciter 5.

[0038] Elements of the unbalance exciter 5 can be a support structure 9, a drive shaft 10, a drive device 11, an unbalance mass element 12, a bearing device 13, a support surface 31, a shaft rotary bearing 20 and / or an eccentric bearing device 15.

[0039] The support structure 9 is a bearing structure on which the drive shaft 10 is rotatably mounted. The support structure 9 can, for example, be designed as a cage or a housing 16. The housing 16 can be designed to completely surround or encapsulate an interior space 21. The housing can comprise a cover element 17 and a cup element 18, which together enclose the interior space 21 and are connected to each other, for example, in a detachable manner. The housing 16 can comprise one or more bottoms 19, which can be formed, for example, by the cover element 17 and / or the cup element 18.

[0040] The drive shaft 10 can be rotated about the vibration excitation rotation axis 8 relative to the support structure 9. For this purpose, the unbalance exciter 5 can have the shaft slewing bearings 20. These can be designed, for example, as plain or rolling bearings, as shown by way of example in the embodiment. Thus, it can be provided that the drive shaft 10 extends, preferably at least partially, along the vibration excitation rotation axis 8 from a first shaft slewing bearing 20, for example formed in the base 19 of the cover element 17, through the interior 21 to a second shaft slewing bearing 20, for example formed in the base 19 of the pot element 18.

[0041] The drive shaft 10 can further comprise a connection geometry, for example a connection flange 22, for example in the form of a shaft end projecting beyond the outside of the housing 13. The output of a [missing information] can be connected to the connection geometry, for example the connection flange 22. Fig. 6 a drive gearbox not shown in detail or a drive motor, in particular an electric motor, can be connected directly.

[0042] The drive unit 11 can be arranged on the drive shaft 10, particularly in a stationary position. It is possible to design the drive unit 11 as a separate component from the drive shaft 10 or as a component formed integrally with the drive shaft 10. The drive unit 11 thus rotates, particularly together with the drive shaft 10, around the vibration excitation rotation axis 8 during the rotational operation of the unbalance exciter 5.

[0043] The drive element 11 can be arranged on the drive shaft 10 such that it projects at least partially from the drive shaft 10 in the radial direction R to the vibration excitation rotation axis 8. For this purpose, the drive element 11 can, for example, comprise one or more elements designed in the form of a material web. In the case described in the Fig. 6 In the illustrated embodiment, the drive device 11 comprises, for example, two such material webs which together form a drive fork 23.

[0044] The unbalance exciter 5 can also include the unbalance mass element 12, which, in this case, is arranged, for example, in the axial direction B of the vibration excitation rotation axis 8 between the two material webs of the drive fork 23 of the drive device 11 and in the radial direction R to the vibration excitation rotation axis 8 next to the drive shaft 10. The unbalance mass element 12 can be mounted on the drive device 11 via the bearing device 13.

[0045] The unbalance mass element 12 can comprise a rotationally symmetrical region and, in particular, can be entirely rotationally symmetrical. More specifically, the unbalance mass element 12 can be at least partially, and especially as a whole, cylindrical or have a cylindrical outer surface. Additionally or alternatively, the unbalance mass element 12 can have rounded outer edges at its end faces in the axial direction of its axis of rotation. It can also, additionally or alternatively, have a convex contour over its entire surface of rotation.

[0046] The bearing assembly 13 can comprise the eccentric rotary bearing assembly 15 and a rolling rotary bearing 24. The rolling rotary bearing 24 has a rolling rotation axis 25, and the eccentric rotary bearing assembly 15 has an eccentric rotation axis 26. The rolling rotation axis 25 and the eccentric rotary bearing assembly 15 can run parallel to the vibration excitation rotation axis 8. The eccentric rotation axis 26 and the rolling rotation axis 25 can, in particular, also run parallel to each other, but especially not coaxially to each other. Even if these two axes 25 and 26 are shown in the illustration according to Fig. 6 lying on a line is due to the fact that the two axes in the Fig. 6 The relative positions shown in the image plane lie one behind the other. This also applies to the... Fig. 6 In the example shown, axes 25 and 26 are therefore not coaxial. This is particularly relevant as explained in more detail below. Figures 7 and 8further illustrate the relative position of the eccentric rotation axis 26 and the roll rotation axis 25.

[0047] The rolling rotation bearing 24 can, for example, also be used as a sliding bearing or, as in the Fig. 6 shown to be designed as a rolling bearing.

[0048] A bearing axis element 27 can extend between the two material webs of the drive unit 11. The unbalanced mass element 12 can be rotatable about this bearing axis element 27 around the rolling rotation axis 25. The bearing axis element 27 can also be rotatable about the rolling rotation axis 25 together with the unbalanced mass element 12 and, for this purpose, can be rotatably mounted, for example, in an eccentric disc described in more detail below, via a rotary bearing. In the axial direction outwards of the rolling rotation axis 25, the bearing axis element 27 can each comprise an eccentric disc 28. These can be designed to be rotationally fixed to the bearing axis element 27. The two eccentric discs 28 can have an outer, in particular cylindrical, surface 29 located radially outwards from the rolling rotation axis 25 and / or eccentric rotation axis 26, which serves as a sliding bearing surface for the eccentric bearing unit 15.The bearing webs of the drive unit 11 can be fitted with receiving bushings for receiving and supporting the eccentric discs 28. The entire assembly, consisting of the bearing axis element 27 and the unbalance mass element 12, can pivot about the eccentric axis of rotation 26 around the eccentric bearings formed by the eccentric bearing unit, thereby allowing the radial distance R1 between the vibration excitation rotation axis 8 and the currently outermost point of the unbalance mass element 12 to be varied within a distance range defined by the eccentric bearing unit 15.

[0049] The unbalance mass element 12 can be rotationally symmetrical about the rolling rotation axis 25. For this purpose, it can, for example, be essentially convex, cylindrical, or spherical. The unbalance mass element 12 has an outer surface 30. This surface can be designed such that its outer contour is circular in cross-section perpendicular to the rolling rotation axis 25.

[0050] Part of the supporting structure 9 can be a support surface 31, formed in particular, for example, by the housing 16, on which the unbalance mass element 12 rolls with its outer surface 30 during rotation of the unbalance exciter 5 around the rolling rotation axis 25 and is supported outwards in the radial direction to the vibration excitation rotation axis 8. The support surface 31 can thus be designed as an inner surface 35, in particular of the housing 16, and in particular as a hollow cylindrical surface. Due to the centrifugal forces acting on the unbalance mass element 12 during rotation, it is pressed outwards in the radial direction R towards the vibration excitation rotation axis 8 in the direction of the drive shaft 10 around the vibration excitation axis 8, towards the support surface 31.

[0051] The eccentric bearing assembly 15, as described above, and the adjustment of the eccentric bearing assembly 15 about the eccentric axis of rotation 26, which is pushed radially outwards by the centrifugal forces and radially inwards by the rolling contact of the unbalanced mass element 12, ensure that the unbalanced mass element 12 remains in contact with the support surface 31 throughout its rotational movement about the vibration excitation rotation axis 8. Manufacturing tolerances and / or tolerances resulting from wear can thus be reliably compensated for.At the same time, practically no tensile forces acting on the drive shaft 10 in the radial direction outwards to the vibration excitation rotation axis 8 due to the unbalance mass element 12 being mounted eccentrically to the drive shaft 10, so that, for example, potential bending loads on the drive shaft 10 are considerably reduced compared to conventional vibration exciters.

[0052] The Figures 7 and 8 These are excerpts from area I. Fig. 6, whereby the pot element 18 is not shown in these illustrations. In addition to the radial distance R1 between the vibration excitation rotation axis 8 and the point of maximum radial distance to this axis of the unbalance mass element 12 in the current rotational position, the figures also show the current radial distance R2 between the vibration excitation rotation axis 8 and the eccentric rotation axis 26, as well as the radial distance R3 between the vibration excitation rotation axis 8 and the rolling rotation axis 25. In the Fig. 7 The eccentric bearing assembly 15 is rotated about the eccentric axis of rotation 26 in such a way that the radial distance R1 is almost minimal and in the Fig. 8The radial distance R1 is almost at its maximum. The radial distance R2 between the vibration excitation rotation axis 8 and the eccentric rotation axis 26 is constant in both relative positions. However, the distance R3, and therefore also the distance R1, differ by the amount ΔR1. In comparison to each other between the Figures 7 and 8 are the distances between R1 and R3 therefore relative to the Fig. 7 in Fig. 8 by the amount ΔR1. In this way, ΔR1 defines a compensation range available in the radial direction R to the vibration excitation rotation axis 8 by means of the eccentric bearing device 15 described above, with which, in particular, a reliable rolling system of the unbalance mass element 12 on the support surface 31 is ensured during rotational operation about the vibration excitation rotation axis 8.

[0053] In principle, it is possible to connect the drive shaft 10, particularly in the area of ​​its connection geometry, and especially its connection flange 22, to an output element of a drive transmission, for example a gear or traction transmission. However, it can also be provided that the drive shaft 10 is directly connected to a drive motor, in particular a hydraulic or electric motor 32, as for example in the Fig. 9 This is illustrated in more detail below, for example, it is directly connected to the rotor of the electric motor 32. It can also be provided that the drive shaft 10 is formed directly by the rotor of the electric motor 32.

[0054] In the Fig. 9It is further apparent that the housing 16 can include a bearing flange 33, via which the unbalance exciter 5 can be arranged on or attached to, for example, a higher-level bearing structure of a soil compaction machine 1, such as, in particular, a disc of a roller drum or a base plate of a vibratory plate compactor. Additionally or alternatively, a bearing flange 34 can be provided or formed on the housing 16, via which the drive motor, in particular the electric motor 32, can be attached, especially directly, to the unbalance exciter 5, in particular to a housing 16 of the unbalance exciter 5.

[0055] The Figures 10 and 11 illustrate, particularly in comparison to each other, a further possible variation in the design of the individual components of the imbalance exciter 5. The one in the Fig. 10 The cross-sectional view shown along the vibration rotation axis 8 refers to the one shown in the Figures 6 to 9discussed embodiment of the unbalance exciter 5. In the Figures 10 and 11 An inner diameter D1 of the inner surface 35 of the interior 21 and an outer diameter D2 of the outer surface 30 of the unbalance mass element 12 are specified. The difference between the two embodiments is that in the Fig. 10 D2 > ½ D1 is and in the embodiment according to the Fig. 11 D2 < ½ D1. In other words, this means that in the embodiment and relative position of the eccentric bearing device 15, as described in the Fig. 10 specified that the unbalance mass element 12, viewed from its outer side opposite the drive shaft 10 in the direction of the drive shaft 10, overlaps the vibration excitation rotation axis 8 or D2 > R1, whereas in the embodiment according to the Fig. 11 This overlap is not present, or D2 < R1. An embodiment according to D2 = ½ D1 is of course also included in the invention.

[0056] In particular, the views of Figures 10 and 11 Figure 1 shows a recess 36 in the drive shaft 10, which can be provided for at least partial reception of the unbalance mass element 12. Compared to the parts of the drive shaft 10 located in the slewing bearing 20, the drive shaft 10 thus has a region in the area of ​​the recess 36 in the axial direction of the vibration excitation rotation axis 8 in which material is removed, particularly in comparison to the shaft parts of the drive shaft 10 positioned in the slewing bearings 20 in the axial direction D of the vibration excitation rotation axis 8. In this region, the drive shaft 10 thus has, in particular at least partially, a smaller and / or radially offset thickness relative to the vibration excitation rotation axis 8 in the radial direction R than seen in the region at the level of the slewing bearings 20.

[0057] It may be preferred if the drive shaft 10, in particular together with the drive element 11, is balanced as a whole and thus has no eccentricity to the vibration excitation rotation axis 8. For this purpose, the drive shaft 10 may have one or more material thickenings 37 on the side that is radially opposite the drive element 11 to the vibration excitation rotation axis 8 ( Fig. 10 ) exhibiting features that counteract an eccentricity caused by the radially projecting drive element 11. In particular, a radially outwardly displaced material area 37 can be provided at the level of the recess 36, either additionally or alternatively, in the axial direction D of the vibration excitation rotation axis 8. Fig. 10 ) are planned.

[0058] The Figures 12 to 14Figure 5 illustrates a further embodiment of an unbalance exciter 5, whereby the differences of this embodiment compared to the previous embodiments are discussed in detail below, and reference is otherwise made to the preceding information on possible embodiments of the unbalance exciter 5. The perspective sectional view according to Fig. 12 For clarity, pot element 18 is not shown.

[0059] A key difference between this embodiment and the previous embodiments is that the unbalance mass element 12 is not formed by a single, continuous unbalance mass, but rather by two partial unbalance mass elements 38a and 38b, ideally identical in construction. Each of these can be rotatably mounted on the bearing axis element 27 about the rolling rotation axis 25 via at least one or more rolling rotation bearings 24. The drive device 11 can be designed as a drive tongue 39, in particular a web-like one, which projects radially towards the vibration excitation rotation axis 8 in the direction of the two partial unbalance mass elements 38a and 38b and is positioned between the two partial unbalance mass elements 38a and 38b in the axial direction of the vibration excitation rotation axis 8.The bearing axle element 27, which in this case supports both partial unbalance mass elements 38a and 38b, can therefore also support both partial unbalance mass elements 38a and 38b centrally via a single eccentric joint or via a single eccentric bearing device 15 with the possibilities of eccentric adjustment or the adjustment possible within the compensation range ΔR1 already described above for the previous embodiments.

[0060] This embodiment may also include a housing 16 with a cover element 17 and a pot element 18, as shown in the Figures 13 and 14 shown, so that the interior space 21 can be encapsulated.

[0061] The Figures 15, 16 and 17The above-described functioning of the bearing device 13 and, in particular, the eccentric device 15 are further illustrated, whereby, for the sake of clarity, only individual parts of the bearing device, as already explained above, are labelled, and reference is made to the preceding description for the rest. Figures 15, 16 and 17 are top views of elements of an unbalance exciter 5 in the axial direction of the vibration excitation rotation axis 8.

[0062] The in the Figures 15, 16 and 17 For clarity, the specified radial distances R1, R2, and R3 are given as vertical distances. The vibration excitation rotation axis 8, the roll rotation axis 25, and the eccentric rotation axis 26 can be parallel, but not coaxial.

[0063] In the Fig. 15 is the distance R1 comparatively small, in the Fig. 16 in a central location and in the Fig. 17comparatively large. The distance R2, i.e., the radial distance of the eccentric rotation axis 26 to the vibration excitation rotation axis 8, is the same in all three adjustment positions. However, rotating the eccentric disk 28 about the eccentric rotation axis 26 changes the relative position of the bearing axis element 27 with respect to its radial distance R3 to the vibration excitation rotation axis 8. In the relative position according to Fig. 15 R2 > R3, according to Fig. 16 is R2 = R3 (W = 0°) and according to Fig. 17 R2 < R3. Because the radial distance R3 remains constant, the maximum radial distance of the radial to the vibration excitation rotation axis 8 of the outer point of the unbalance mass element 12, given by R2, thus varies depending on the rotational position of the eccentric disk 28 or thus of the eccentric bearing assembly 15.

[0064] The rotational position of the eccentric disk relative to a virtual connecting line H of the rolling rotation axis 25 with the eccentric rotation axis 26 in a virtual reference plane perpendicular to these axes is indicated in the figures with the angle W relative to a virtual horizontal reference line. The angle W in the neutral position is given by the Fig. 16 0°. If the eccentric rotary device is adjusted such that the radial distance R3 decreases, the angular magnitude of W increases by a rotation angle, in this case, for example, approximately 50°, as in the Fig. 15 shown. If the eccentric rotary device is adjusted such that the radial distance R3 increases, the angular magnitude of W starting from the relative position in Fig. 16 by an angle of rotation, in this case also by approximately 50°, as for example in the Fig. 17 depicted.

[0065] The setting of the current rotational position of the eccentric device 15 can depend in particular on the current radial distance of the support surface 31 to the vibration excitation rotation axis 8. If, for example, changes occur during one revolution on the vibration excitation rotation axis 8 due to potentially existing manufacturing and / or wear tolerances, these can be compensated for by a rotational movement of the eccentric bearing device 15, specifically, for example, the eccentric disc 28, while maintaining contact of the unbalance mass element 12 within the compensation range ΔR1, as shown in the Figures 15, 16 and 17 shown, balanced.

[0066] Especially also the Figures 15, 16 and 17further illustrate that the unbalance mass element 12 can be supported on the support surface 31 in the radial direction to the vibration excitation rotation axis 8, so that practically no centrifugal force-induced tensile forces are transmitted from the unbalance mass element 12 to the drive device 11 and the drive shaft 10.

[0067] In the Figures 15, 16 and 17 For clarity, the course of the support surface 31 is partially indicated schematically. The direction of rotation of the drive shaft 10 around the vibration excitation rotation axis 8 is shown in the Figures 15, 16 and 17The direction of rotation is indicated by the arrow symbolizing the support surface 31 and is therefore counterclockwise in this view. The rolling rotation axis 25, viewed in the direction of rotation, is always located behind a radial connecting line G extending from the vibration excitation rotation axis 8 to the eccentric rotation axis 26. This means that the drive device 11 pulls the unbalance mass element 12 along during rotation and does not push it, although a pushing arrangement is also possible and included in the invention, regardless of the specific embodiment.

[0068] Fig. 18Figure 1 shows a side view of a rolling drum 40. This drum comprises a drum sleeve 41 and, for example, a bearing device arranged in the inner sleeve of the rolling drum 40, for example, in the form of a disc 42. The bearing device can have several, for example, four, receiving devices, for example, bearing flanges 43, to each of which an unbalance exciter unit 5.1, 5.2, 5.3, 5.4 is arranged. Each of the unbalance exciter units 5.1, 5.2, 5.3, 5.4 can have its own drive motor. These individual drive motors can be controlled individually, but in particular coordinated with each other, by a control unit 44 in order to be able to set and vary different vibration characteristics of the rolling drum 40, such as circular excitation, directional vibration, or oscillatory vibration, in rotational operation by means of the interaction of the several unbalance exciter units 5.1, 5.2, 5.3, 5.4.

[0069] Fig. 19illustrates the roller bandage from the Fig. 18 in a cross-sectional view along line II-II from the Fig. 18 Due to the relatively compact design of the individual unbalance exciters 5, not only can several of the unbalance exciters 5 be arranged on, for example, a disc 42, but several of these discs, each with several of these unbalance exciters 5, can also be arranged simultaneously in a roller drum 40. It is then at least preferred if the individual unbalance exciters 5 are positioned one behind the other, viewed in the direction of a rotation axis C of the roller drum 40, and, viewed in the direction of the rotation axis C, are positioned at the same angular position and / or radial distance to this rotation axis.

[0070] In the embodiment according to the Figures 20 and 21 are similar to the embodiment of the Figures 18 and 19Several unbalance exciter units 5 are arranged per disc 42 in a rolling drum. However, in this case, exactly two unbalance exciter units 5.1 and 5.3 are present per disc 42. The respective unbalance exciter units 5.1 and 5.3 of the respective discs 42 are also arranged in the rolling drum 40 such that a vibration excitation rotation axis 8 of an unbalance exciter unit 5 of one disc 42 is coaxial with the vibration excitation rotation axis 8 of an unbalance exciter unit 5 of the other disc 42.

[0071] All of the unbalance exciter units 5 can have the same radial distance to the axis of rotation C of the roller bandage 42 with their respective vibration excitation rotation axes 8.

[0072] All of the unbalance exciter units 5 of a roller drum 42 can be of identical construction. Reference symbol list

[0073] 1 Soil compaction machine 2 Machine frame 3 Drive unit 4 Soil contact device 5 Unbalance exciter 6 Operator's platform 7 Travel device 8 Vibration excitation rotation axis 9 Support structure 10 Drive shaft 11 Drive device 12 Unbalance mass element 13 Bearing device 15 Eccentric bearing device 16 Housing 17 Cover element 18 Pot element 19 Ground 20 Shaft swivel bearing 21 Interior 22 Connection flange 23 Drive fork 24 Roller rotation bearing 25 Roller rotation axis 26 Eccentric rotary axis 27 Bearing axis element 28 Eccentric disc 29 Outer surface of eccentric disc 30 Outer surface of unbalance mass element 31 Support surface 32 Electric motor 33 Bearing flange 34 Bearing flange 35 Inner surface 36 Recess 37 Material thickening 38a,38b Partial unbalance mass elements 39 Drive tongue 40 Rolling bandage 41 Bandage sleeve 42 Disc wheel 43 Bearing flange 44 Control unit A Working / movement direction B Axial direction C Rotation axis of rolling bandage G Connecting line H Connecting line R Radial direction R1 Radial distance between vibration excitation rotation axis and outermost point of the unbalance mass element R2 Radial distance between the vibration excitation rotation axis and the eccentric rotation axis R3 Radial distance between the vibration excitation rotation axis and the rolling rotation axis ΔR1 Compensation range D1 Inner diameter Interior 21 D2 Outer diameter of unbalance mass element W Angle,

Claims

1. Unbalance exciter (5) for a soil compaction machine (1), comprising - a support structure (9), - a drive shaft (10) rotatable about a vibration excitation rotation axis (8) relative to the support structure (9);- a drive unit (11) rotating with the drive shaft (10) about the vibration excitation rotation axis (8), - an unbalanced mass element (12) which is rotatable relative to the drive unit (11) about a rolling rotation axis (25), wherein the unbalanced mass element (12) is connected to the drive unit (11) via a bearing assembly (13), so that the drive unit (11) rotates together with the unbalanced mass element (12) rotating about the rolling rotation axis (25) about the vibration excitation rotation axis (8), - a support surface (31) extending substantially circularly around the vibration excitation rotation axis (8), against which the unbalanced mass element (12) bears outwards in the radial direction (R) to the vibration excitation rotation axis (8) and on which the unbalanced mass element (12) rotates during rotation of the drive shaft (10) about the The vibration excitation rotation axis (8) rolls and rotates around the roll rotation axis (25), ; characterized by that The bearing assembly (13) between the drive assembly (11) and the unbalance mass element (12) has an eccentric bearing assembly (15) with an eccentric rotation axis (26) which is designed such that the radial distance (R) of the rolling rotation axis (25) to the vibration excitation rotation axis (8) is adjustable within a compensation range (ΔR1) defined by the eccentric bearing assembly (15).

2. Imbalance exciter (5) according to claim 1, characterized by that the vibration excitation rotation axis (8), the roll rotation axis (25) and the eccentric rotation axis (26) run parallel to each other.

3. Imbalance exciter (5) according to any one of the preceding claims, characterized by that the drive shaft (10) is mounted relative to the support structure (9) and / or the unbalance mass element (12) is mounted relative to the drive shaft (10) via a rolling bearing, in particular a deep groove ball bearing.

4. Imbalance exciter (5) according to any one of the preceding claims, characterized by that the bearing device (13) comprises a bearing axis element (27) extending longitudinally in the direction of the rolling rotation axis (25), and an eccentric disc (28) of the eccentric bearing device (15) is connected to the bearing axis element (27) in a rotationally fixed manner.

5. Imbalance exciter (5) according to any one of the preceding claims, characterized by thatthe drive device (11) is designed as a drive fork (23) with two bearing projections spaced apart in the axial direction (D) of the vibration excitation rotation axis (8) and projecting in the radial direction (R), and that the unbalance mass element (12) is mounted on the bearing projections between the two bearing projections in the axial direction (D) of the vibration excitation rotation axis (8) and / or that the drive device (11) is designed as a drive tongue (39) with a bearing projection spaced apart in the axial direction (D) of the vibration excitation rotation axis (8) and projecting in the radial direction (R), and that the unbalance mass element (12) has two partial unbalance mass elements (38a, 38b) positioned one behind the other in the axial direction of the vibration excitation rotation axis (8), which are mounted on opposite sides of the bearing projection.

6. Imbalance exciter (5) according to any one of the preceding claims, characterized by thatthe unbalance mass element (12) has at least a partially cylindrical outer circumferential surface (30) and / or the support surface (31) has one or more hardened running rings.

7. Imbalance exciter (5) according to any one of the preceding claims, characterized by that a maximum radial outer diameter (D2) of the unbalance mass element (12) is greater than half of a maximum inner diameter (D1) of the circular support surface (31).

8. Imbalance exciter (5) according to any one of the preceding claims, characterized by that the drive shaft (10) has a recess (36) extending in the radial direction (R) and in the axial direction (D) of the vibration excitation rotation axis (8) for at least partial accommodation of the unbalance mass element (12).

9. Imbalance exciter (5) according to any one of the preceding claims, characterized by thatThe unbalance exciter (5) comprises a housing (16) forming the support structure (9), wherein the housing (16) has, in particular, at least one of the following features: - It has a bearing flange (33) for attaching the unbalance exciter (5) to a higher-level bearing structure; - It comprises a cover element (17) and a cup element (18), wherein a shaft swivel bearing (20), in particular in the form of a rolling bearing, is provided in the base (19) of the cover element (17) and in the base (19) of the cup element (18); - It has an interior space (21) sealed to the outside environment, the wall surface of which forms at least part of the support surface (31).

10. Imbalance exciter (5) according to any one of the preceding claims, characterized by that the drive shaft (10) is directly connected to an electric motor (32) and / or, in particular, is non-rotatably connected to a rotor of an electric motor (32).

11. Roller bandage (40) with a substantially hollow cylindrical bandage shell (41) and with at least one unbalance exciter (5) arranged in an interior of the bandage shell (41) according to one of claims 1 to 13, wherein the unbalance exciter (5) comprises: - a support structure (9), - a drive shaft (10) rotatable about a vibration excitation rotation axis (8) relative to the support structure (9); - a drive unit (11) rotating with the drive shaft (10) about the vibration excitation rotation axis (8), - an unbalance mass element (12) which is rotatable about a rolling rotation axis (25) relative to the drive unit (11), in particular a rolling rotation axis (25) extending parallel to the vibration excitation rotation axis (8), wherein the unbalance mass element (12) is connected to the drive unit (11) via a bearing assembly (13),so that the drive device (11) together with the unbalanced mass element (12) rotating about the rolling rotation axis (25) rotates about the vibration excitation rotation axis (8), and - a support surface (31) extending essentially circularly around the vibration excitation rotation axis (8), against which the unbalanced mass element (12) bears outwards in the radial direction to the vibration excitation rotation axis (8) and on which the unbalanced mass element (12) rolls in a rotational operation of the drive shaft (10) about the vibration excitation rotation axis (8) and thereby rotates about the rolling rotation axis (25).

12. Roller bandage (40) according to claim 11, characterized by that it (40) comprises at least two of the unbalance exciters (5), wherein the at least two unbalance exciters (5) are in particular arranged in the interior of the roller band (40) such that the vibration excitation rotation axes (8) of the at least two unbalance exciters (5) run parallel to each other.

13. Roller bandage (40) according to one of claims 11 or 12, characterized by that it (40) has four imbalance agents (5) arranged in a common plane.

14. Soil compaction machine (1) with one or more unbalanced exciters (5) according to one of claims 1 to 10 and / or with one or more roller drums (40) according to one of claims 11 to 13.

15. Soil compaction machine (1) according to claim 14, characterized by that a control unit is provided which is designed to control the direction of rotation and / or the rotational frequency of the drive shafts (10) of the at least two unbalance exciters (5) about their respective vibration excitation rotation axis (8), in particular individually.

16. Soil compaction machine (1) according to one of the sprays 14 or 15, characterized by that it is a tandem roller, in particular a articulated or articulated roller, a roller train, a trench roller or a vibratory plate.

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