Vibration exciter for a soil compaction machine and soil compaction machine

Abstract

The invention relates to a vibration exciter (100) for a soil compaction machine, comprising such a vibration exciter. The vibration exciter (100) includes a balanced exciter shaft (110) with a stop (115) for a counterweight (120). The exciter shaft (110) has an exciter shaft axis of rotation (111) about which the exciter shaft (110) is rotatable. Furthermore, the vibration exciter (100) includes the counterweight (120), which is arranged to rotate relative to the exciter shaft (110) about an unbalance axis of rotation (112). The exciter shaft axis of rotation (111) is offset from the unbalance axis of rotation (112) by a radial offset (V). r ) arranged in a staggered pattern.

Description

[0001] The invention relates to a vibration exciter (or a device for vibration excitation) for a soil compaction machine. The invention further relates to a soil compaction machine with at least one such vibration exciter.

[0002] Vibration exciters of this type are used particularly in self-propelled and / or hand-operated soil compaction machines, such as vibratory plates and rollers. Such soil compaction machines with a vibration exciter are described, for example, in EP 2 881 516 A1. Details of known vibration exciters are known, for example, from the publications DE 10 2014 116 659 B4, US 4,830,534 A, US 6,224,293 B1, EP 0 053 598 B1, EP 2 390 416 B1, DE 20 2016 103 865 U1 and DE 10 2020 132 973 A1.

[0003] The purpose of the arrangement described in DE 10 2014 116 659 B4 is to create a two-amplitude eccentric shaft that has a low moment of inertia about the axis of rotation around which it is to rotate. In the eccentric shaft according to DE 10 2014 116 659 B4, the cross-sections of the fixed and movable eccentric masses of the eccentric shaft must be arranged such that they are enclosed in a circular shape when the masses interact. The circular shape must coincide with the intersection of the axis of rotation with the plane of intersection or be located in its immediate vicinity. A disadvantage of the eccentric shaft according to DE 10 2014 116 659 B4 is that at small amplitudes, a relatively high moment of inertia is present due to the "dead mass" that rotates along with the shaft, i.e., the mass that does not contribute to the eccentricity of the overall arrangement.

[0004] US 4,830,534 A relates to a vibrator suitable for use in a compaction machine that can produce either relatively high or relatively low vibration amplitudes over a frequency range. The vibrator according to US 4,830,534 A automatically assumes the low amplitude setting when the rotor slows down to minimize the energy required to start and stop the rotor and the impact on the compacted surface. This is achieved by a rotor that includes a rotor shaft with an eccentric weight attached to it. The weight can move radially away from the rotor shaft but is pressed toward the rotor shaft by a spring mechanism. A locking mechanism, responsive to the direction of rotation of the rotor, restrains the radial movement of the eccentric weight to produce a low amplitude setting when the rotor is turned in one direction.When the rotor is turned in the opposite direction, the locking mechanism of the eccentric weight is released, allowing the centrifugal force to move the eccentric weight away from the rotor shaft and create a high-amplitude setting. When the rotor is stopped or slowed to a standstill in the high-amplitude setting, the spring force returns the eccentric weight to the low-amplitude position, thus reducing the required starting and stopping energy and the effects of this process on the surface being compacted. The disadvantages of the vibration generator according to US 4,830,534 A are that a large amplitude is only usable at high frequencies (with frequency-dependent switching), which leads to extreme surface pressures on cams and cam tracks, as well as highly stressed bearings for the unbalanced mass. This ultimately results in increased wear.

[0005] US 6,224,293 B1 relates to a variable-amplitude vibrator for a compaction machine used in road construction. The vibrator according to US 6,224,293 B1 comprises a weight element and a shaft rotatable about an axis of rotation. The shaft extends longitudinally through the weight element and has a mounting area where the weight element is mounted. The vibrator also includes a positioning arm engaged with the weight element and rotatable about the axis of rotation relative to both the shaft and the weight element. The rotation of the positioning arm relative to the shaft and the weight element moves the weight element in a radial direction orthogonal to the axis of rotation relative to the shaft, thereby changing the moment of inertia of the weight element about the axis of rotation and producing a different vibration amplitude during the rotation of the weight element.The disadvantages of the vibration generator according to US 6,224,293 B1 are also high surface pressures on cams and cam tracks, a highly stressed bearing of the unbalanced mass, which can lead to wear, as well as translational movements between the drive shaft and the unbalanced mass during switching.

[0006] EP 0 053 598 B1 relates to a method for compacting a layer of material by moving a compaction device with at least one drum over said layer, wherein the drum acts on the layer by gravity and a vibration force. The vibration force is exerted by applying a substantially pure alternating torque to the drum and its axis. A disadvantage of the invention described in EP 0 053 598 B1 is that independent control of the oscillation and circular excitation amplitude is not possible.

[0007] EP 2 390 416 B1 proposes a device for vibration excitation for a soil compaction machine. According to the invention described in EP 2 390 416 B1, the axes of rotation of the exciter weight attached to the exciter shaft and the counterweight are not coaxial, so that the counterweight can pivot on a path of rotation eccentric to the axis of rotation of the exciter shaft. This offset of the axes of rotation ensures a clear reversal and a corresponding change in amplitude, even if the counterweight should rebound after impact. A disadvantage of the vibration excitation device according to EP 2 390 416 B1 is that, due to the addition / subtraction of masses to generate large / small amplitudes, a relatively high moment of inertia is present, particularly at small amplitudes due to the entrained "dead mass".

[0008] DE 20 2016 103 865 U1 deals with a vibratory roller assembly comprising a roller, a motor operationally connected to the roller, a drive shaft driven by the motor, an eccentric with a fixed mass connected to a second rotating shaft inside the roller, and an eccentric with a variable mass connected to a third rotating shaft inside the roller. The second and third rotating shafts are rotatably connected to the drive shaft. As with EP 0 053 598 B1, a disadvantage of DE 20 2016 103 865 U1 is that independent control of the oscillation and circular excitation amplitude is not possible.

[0009] DE 10 2020 132 973 A1 relates to a compaction roller for a soil compactor, comprising a roller shell rotatable about a roller axis of rotation and enclosing an interior space of the roller, as well as an oscillation / vibration arrangement located in the interior space of the roller. A disadvantage of the arrangement described in DE 10 2020 132 973 A1 is that two counterweights are required for switching between vibration and oscillation in order to generate different imbalances and thus represent adapted amplitude values ​​for vibration and oscillation.

[0010] The object of the present invention is to provide a vibration exciter for a soil compaction machine which is improved with regard to one or more disadvantages known from the prior art.

[0011] The problem is solved with a vibration exciter for a soil compaction machine and with a soil compaction machine according to the independent claims. Preferred embodiments are specified in the dependent claims.

[0012] According to a first aspect of the invention, a vibration exciter is provided for a soil compaction machine. The vibration exciter is thus a device, particularly also designed as a module, which, when used as intended, especially in a soil compaction machine, particularly of the vibratory plate or roller type, is designed to subject a soil contact device, for example a base plate or a roller drum, to vibrations. It can be provided, in particular, that the vibration exciter is directly and undamped connected to the soil contact device.

[0013] The vibration exciter comprises at least one balanced exciter shaft with a stop for at least one counterweight. The exciter shaft also has an exciter shaft axis of rotation about which it can rotate. An "exciter shaft" can be understood as a shaft or component used to generate oscillations or vibrations by means of a rotational movement of the shaft, indirectly via an imbalance coupled to the shaft. A "balanced exciter shaft" can be understood as an exciter shaft designed such that no undesirable fluctuations or asymmetrical forces occur during rotation about its axis of rotation, in particular, no fluctuations or asymmetrical forces occur at all. Typically, the exciter shaft is thus balanced with respect to its axis of rotation. The "exciter shaft axis of rotation" can be understood as an axis of rotation about which the exciter shaft rotates in a balanced manner.The excitation shaft can thus be designed such that it is entirely free of any imbalance or eccentricity effective during rotation with respect to its axis of rotation. In particular, the excitation shaft is typically designed such that amplitudes and phases potentially caused by rotation cancel each other out or compensate for each other, especially due to differently designed sections of the excitation shaft along its axis of rotation. In other words, the excitation shaft itself has no imbalance. Specifically, the center of mass of the excitation shaft lies on the excitation shaft's axis of rotation.

[0014] Furthermore, the vibration exciter includes the counterweight, which is rotatably arranged relative to the exciter shaft about an unbalance axis. An "unbalance axis" can be understood as an axis of rotation around which the counterweight rotates around the exciter shaft. The counterweight can be mounted on the exciter shaft in such a way that it is precisely unbalanced with respect to both the exciter shaft's axis of rotation and the unbalance axis, thus exhibiting an eccentricity with respect to both axes simultaneously. In the vibration exciter, the desired unbalance or eccentricity of the entire assembly of exciter shaft and counterweight is therefore provided by the counterweight, and specifically not by the exciter shaft itself, not even partially.The mounting of the counterweight on the excitation shaft is designed such that the distance of the counterweight's center of mass relative to the unbalance axis remains constant during rotation of the counterweight around the unbalance axis. The radial distance of the counterweight's center of mass is therefore constant regardless of the counterweight's rotational position relative to the unbalance axis.

[0015] The range of motion of the counterweight around the unbalance axis relative to the exciter shaft is limited depending on the direction of rotation. The counterweight can therefore only rotate around the unbalance axis within a limited adjustment range, for example, up to a maximum of 180° relative to the exciter shaft. This rotation limitation is achieved by a stop on the exciter shaft against which the counterweight strikes during relative adjustment, particularly with a counter-stop. This stop can, for example, be a stop formation projecting radially towards adjacent surfaces and / or areas of the exciter shaft. It may be designed so that the counterweight can strike this stop on both sides, depending on the current direction of rotation of the exciter shaft. Alternatively, two separate stop formations, spatially separated from each other in the direction of rotation of the exciter shaft, may be provided.

[0016] According to the invention, the vibration exciter is designed such that the exciter shaft's axis of rotation is offset from the unbalance axis of rotation of the counterweight by a radial offset Vr, and in particular, is offset by the radial offset Vr and runs parallel to the unbalance axis. The radial offset Vr is application- and / or parameter-dependent. It can, for example, be in a range of 1 mm ≤ Vr ≤ 30 mm, and in particular 5 mm ≤ Vr ≤ 15 mm. The radial offset is determined in particular in a virtual reference plane through which the unbalance axis and / or the exciter shaft's axis of rotation run perpendicularly.

[0017] This advantageously provides a vibration exciter which has advantages over excitation systems known from the prior art, in particular with regard to mass distribution, mass inertia, material utilization, power requirement when accelerating the imbalances, and acceleration time until the target frequency is reached.

[0018] In prior art excitation systems, counterweights are used to generate different amplitudes. The center of mass of these counterweights can be shifted relative to a base unbalance shaft. By adding or subtracting the masses of the base unbalance and the counterweight at their respective end positions, which depend on the direction of rotation, different resulting total unbalances of the excitation shaft and counterweight assembly can be achieved. However, in such methods, when using small amplitudes, the mass used for subtracting the total mass must be rotationally accelerated, without this mass contributing to amplitude generation. Furthermore, in prior art excitation systems, the requirement for symmetry of the differential masses often results in an unfavorable mass distribution during additive operation (large unbalance).Overall, conventional technical solutions result in inefficient material utilization and consequently increased power consumption when accelerating the rotational imbalances, or a longer acceleration time until the target frequency is reached. Such disadvantages can be avoided or at least reduced with the vibration exciter according to the invention.

[0019] According to a preferred embodiment, the radial offset V r between the excitation shaft axis of rotation and the unbalance axis of rotation of the counterweight by a first offset V x and a second offset V y is formed, with the second offset V y perpendicular to the first offset V x runs, in particular in a virtual reference plane through which the unbalance axis of rotation and / or the excitation shaft axis of rotation run perpendicularly. The first offset V x can be greater than, less than, or equal to the second offset Vy be. It is preferred if V y < V x is.

[0020] The first offset V x can be in the range of 1 to 20 mm and / or the second offset V y in the range of 1 to 10 mm. Vx can determine the difference in imbalance between the two end positions and Vy the positional stability of the unbalanced mass in its end positions.

[0021] Preferably, the stop for the counterweight is integrally formed with the exciter shaft. In other words, the stop can be formed as a single piece with the exciter shaft, particularly from a single piece of the same material. For manufacturing purposes, the exciter shaft, including the stop, can therefore be a single casting, which may require partial machining. Alternatively, it can be a welded and / or machined part.

[0022] According to a preferred embodiment, in a first position of the counterweight, there is a first distance between the exciter shaft's axis of rotation and the counterweight's center of mass. In a second position of the counterweight, there is preferably a second distance between the exciter shaft's axis of rotation and the counterweight's center of mass, wherein the second distance differs from the first distance. Typically, the second distance is greater than the first. The distance is determined, in particular, by projecting the exciter shaft's axis of rotation and the center of mass onto a common virtual reference plane that is perpendicular to the exciter shaft's axis of rotation.

[0023] It can be provided that, when the exciter shaft rotates in a first direction, the counterweight strikes a first stop surface of the stop in the first position. When the exciter shaft rotates in the opposite direction, the counterweight preferably strikes a second stop surface of the stop in the second position. The first and second stop surfaces can be arranged opposite each other in the direction of rotation of the exciter shaft. In particular, the first and second stop surfaces can be arranged essentially parallel to each other. However, they can also be inclined and / or curved, for example.Additionally or alternatively, it is possible that the first and second stop surfaces are formed by a common stop feature, in particular by a common projection extending radially towards the unbalance axis of rotation relative to adjacent areas of the exciter shaft. It may also be provided, additionally or alternatively, that the exciter shaft axis of rotation runs in a virtual reference plane in which either the first or the second stop surface is also located.

[0024] Additionally or alternatively, the stop can be provided by a first stop and a second stop, the second stop being axially spaced from the first stop along the exciter shaft's axis of rotation. In this case, the stop can thus comprise two individual stops, which, however, act in the same direction with respect to the direction of rotation of the counterweight relative to the exciter shaft. Preferably, the exciter shaft has a recess between the first stop and the second stop. Providing such a recess advantageously reduces the moment of inertia. By using two or more such stops spaced axially apart and acting in the same direction of rotation with respect to the counterweight, it is possible to distribute the stop load or the forces occurring during the stop and / or dragging of the counterweight in the axial direction of the unbalanced axis of rotation.

[0025] According to a preferred embodiment, the counterweight surrounds the exciter shaft in the circumferential direction to at least 25%, in particular to at least 30%, or even to at least 40%. Although a wide variety of variations are generally possible with regard to the specific shape, it is advantageous if the counterweight is designed in the form of a cylindrical segment.

[0026] The vibration exciter can be designed as a vibration exciter module or vibration exciter unit, in particular comprising a support structure, especially for mounting the exciter shaft, and / or a housing. The vibration exciter module can further have a connection point, for example a drive flange, particularly on an end face of the exciter shaft, via which a drive connection is made directly to a drive motor, in particular an electric or hydraulic motor, or to an output of a drive gearbox. The vibration exciter module itself can additionally or alternatively already include the drive motor. For this purpose, it can be provided that the drive motor is additionally and structurally separate from the vibration exciter. It is also additionally or alternatively possible to design or use the exciter shaft as part of an electric motor, in particular as a rotor.Even then, it is important to ensure that the excitation shaft remains balanced overall, including any other potential components of the electric motor, such as windings and / or magnets, etc.

[0027] Another aspect of the invention relates to a soil compaction machine with at least one vibration exciter, in particular a vibration exciter module, according to the embodiments described herein. Such a soil compaction machine can be, in particular, a hand-operated soil compaction machine, such as a vibratory plate compactor or a hand-operated roller, or a self-propelled soil compaction machine, such as a trench roller, a tandem roller, or a roller compactor.

[0028] As can be seen from the embodiments described below, the invention provides a vibration exciter for a soil compaction machine which offers advantages over excitation systems known from the prior art, in particular with regard to mass distribution, inertia, material utilization, power requirement when accelerating the unbalanced masses, and acceleration time until the target frequency is reached. With the vibration exciter according to the invention, in particular, two different unbalanced masses can be generated, and thus, in practical operation, two amplitudes can be generated at the same rotational speed.Compared to conventional excitation systems, in which different imbalances are achieved by adding and subtracting masses, the vibration exciter according to the invention has a reduced moment of inertia, which has a positive effect on the power requirement for accelerating the imbalance and the acceleration time until the target frequency is reached. Advantageously, the vibration exciter according to the embodiments described herein can be used for all common methods of vibration generation. In particular, the vibration exciter can be used at least individually as a pure circular exciter with two amplitudes. Furthermore, the vibration exciter can be used at least twice as a directional vibrator with two amplitudes. Additionally, the vibration exciter can be used at least twice as an oscillating vibrator with two amplitudes.Furthermore, the vibration exciter can also be used in conjunction with a static excitation shaft as a switchable vibration / oscillation oscillator. In addition, compared to excitation systems known from the prior art, the vibration exciter has a simple design with comparatively few components.

[0029] Therefore, one aspect of the invention is also to use at least one vibration exciter according to the invention in a two-amplitude directional oscillator, a switchable oscillation bandage or a switchable circular exciter.

[0030] The invention is explained in more detail below with reference to the exemplary embodiments shown in the figures. The figures schematically show: Fig. 1: a cross-sectional view in a rotation axis of a vibration exciter according to embodiments of the present disclosure, wherein the counterweight is shown in a first position P1; Fig. 2: the cross-sectional view of the vibration exciter made of Fig. 2, where the turnover weight is shown in a second position P2; Fig. 3: Cross-sectional view of the vibration exciter made of Fig. 1, where the turnover weight is shown in a first position P1 and as a dashed line in a second position P2; and Fig. 4: a perspective view of an excitation wave according to an embodiment of the present disclosure.

[0031] The following describes various embodiments, one or more examples of which are shown in each figure. Each example serves for illustrative purposes and is not to be understood as a limitation. For example, features shown or described as part of one embodiment can be used on or in combination with any other embodiment to obtain a further embodiment. It is intended that this disclosure includes such modifications and variations.

[0032] In the following description of the figures, the same reference numbers refer to the same or functionally equivalent components. Generally, only the differences between the individual embodiments are described. Unless otherwise stated, the description of a part or aspect in one embodiment may also refer to a corresponding part or aspect in another embodiment.

[0033] The Fig. Figures 1 to 3 are representations of a vibration exciter 100 in a projection plane corresponding to the image plane. This projection plane runs perpendicular to an exciter shaft rotation axis 111, which will be explained in more detail below, or the exciter shaft rotation axis is perpendicular to this projection plane.

[0034] Fig. Figure 1 shows a schematic view of a vibration exciter 100 for a soil compaction machine according to an embodiment of the present disclosure, in an end-face view. The vibration exciter 100 comprises an exciter shaft 110, which is balanced, in particular with respect to an exciter shaft rotation axis, and a stop 115 for a counterweight 120. The stop 115 can, for example, be integrally formed with the exciter shaft 110. Alternatively, the stop 115 can be provided by a separate component which is attached to the exciter shaft 110.

[0035] The excitation shaft 110 has an excitation shaft rotation axis 111 or is rotatable about it (when used as intended). Fig. In this context, a circular or rotationally symmetrical, for example cylindrical, bearing surface 114 is indicated by a dashed line. This bearing surface thus denotes, in particular, a surface over which the exciter shaft is held in a rotary bearing of a higher-level bearing assembly, for example a support housing, and can be driven, for example, by means of a drive motor or a drive train output. Typically, the center of mass 113 of the exciter shaft 110 lies on the exciter shaft's axis of rotation 111, whereby the exciter shaft is not, in particular, continuously cylindrical and rotationally symmetrical with respect to the exciter shaft's axis of rotation 111, but rather exhibits three-dimensional deformations extending in the axial direction, as described in more detail below. However, the deformations are balanced in such a way that the exciter shaft as a whole is balanced with respect to the exciter shaft's axis of rotation 111.

[0036] Furthermore, the vibration exciter 100 includes the counterweight 120, which is arranged to rotate relative to the excitation shaft 110 about an unbalance axis 112. Fig. Figure 1 shows the counterweight 120 in a first position P1, which results, for example, from rotation of the excitation shaft 110 in a direction of rotation 121 opposite to the clockwise direction.

[0037] In Fig. Figure 2 shows the counterweight 120 in a second position P2, which results, for example, from rotating the excitation shaft 110 clockwise 122. Fig. 3 is the turnover weight in the first position P1 and shown with a dashed line in the second position P2.

[0038] As exemplified in the Fig. 1, Fig. 2 and Fig. As shown in Figure 3, the exciter shaft rotation axis 111 of the exciter shaft 110 is offset from the unbalance rotation axis 112 by a radial offset V. rThe radial offset (Vr) is typically in a range of x1 mm ≤ Vr ≤ y1 mm, in particular x2 mm ≤ Vr ≤ y2 mm.

[0039] According to a preferred embodiment, the radial offset V r by a first offset V x and a second offset V y formed, as exemplified in the Fig. 1 to 3 are shown. The first offset V x can be larger than the second offset V y be. Alternatively, the first offset V x smaller than the second offset V y be. According to another alternative, the first offset V x equal to the second offset Vy. V y is preferably smaller than V x .

[0040] It may be provided that the first offset V x in the x-direction and the second offset V y extends in the y-direction. The second offset V yis therefore perpendicular to the first offset V x For further illustration, a corresponding coordinate system with x-axis and y-axis is shown in the figures. The radial direction r originates from the unbalance axis 112 of the counterweight 120. Typically, the origin of the coordinate system referred to in this disclosure lies on the unbalance axis 112 of the counterweight 120.

[0041] The first offset V x can be in the range of 1 to 20 mm and / or the second offset V y The difference lies in the range of 1 to 10 mm. Vx can determine the difference in imbalance between the two end positions, and Vy can determine the positional stability of the unbalanced mass in its end positions.

[0042] As in the Fig. 1, Fig. 2 and Fig. As shown in Figure 3, the counterweight 120 can be designed such that it surrounds the excitation shaft 110 in the circumferential direction to at least 25%, in particular to at least 30%, or even to at least 40%. In this way, a comparatively compact overall arrangement can be achieved. For this purpose, the counterweight 120 can be designed as a cylindrical segment and / or as a hemispherical shell.

[0043] As in the Fig. 1 and Fig. The position shown in figure 3 is in a first position P1 of the counterweight 120, for example when the excitation wave rotates counterclockwise (see arrow 121 in the Fig. 1 and Fig. 3), typically a first distance E1 exists between the excitation shaft rotation axis 111 of the excitation shaft 110 and the center of mass 123 of the counterweight 120. In a second position P2 of the counterweight, for example when the excitation shaft 110 rotates clockwise (see arrow 122 in the Fig. 2 and Fig. 3) Typically, a second distance E2 exists between the exciter shaft's axis of rotation 111 and the center of mass 123 of the counterweight 120, which differs from the first distance E1. Ideally, the second distance E2 is greater or less than the first distance E1. The second distance E2 results from the sum of the radial distance E0 of the center of mass 123 of the counterweight 120 from the unbalance axis of rotation 112 and the distance in the x-direction of the radial offset V. r between the unbalance axis of rotation 112 of the counterweight 120 and the excitation shaft axis of rotation 111, as can be seen from the Fig. 2 and Fig. 3 emerges.

[0044] As in Fig. As illustrated in Figure 1, the counterweight 120 typically strikes a first stop surface 116 of the stop 115 in the first position P1, particularly when the excitation shaft 110 rotates in a first direction 121, which can be, for example, counterclockwise. When the excitation shaft 110 rotates in a second direction 122 opposite to the first, for example, clockwise, the counterweight 120 strikes a second stop surface 117 of the stop 115 in the second position P2.

[0045] It can be advantageous if the first stop surface 116 and the second stop surface 117 are arranged opposite each other. In particular, the first stop surface 116 and the second stop surface 117 can be arranged essentially parallel to each other or at an angle to each other.

[0046] As exemplified in Fig. As shown in Figure 4, the stop 115 can be provided by a first stop 115A and a second stop 115B. The second stop 115B can be arranged axially spaced from the first stop 115A along the exciter shaft's axis of rotation 111. Furthermore, the exciter shaft 110 can have a recess 130 between the first stop 115A and the second stop 115B, which advantageously leads to a reduction in the moment of inertia.

[0047] Fig. Figure 4 illustrates independently that the exciter shaft 110 typically has radial bearing surfaces 114 at both ends for supporting the exciter shaft. The radial bearing surfaces 114 for supporting the exciter shaft are usually cylindrical. Furthermore, radial bearing surfaces 124 for supporting the counterweight are typically provided, which may also be cylindrical. The radial bearing surfaces 124 for supporting the counterweight may be located closer to the recess 130 than the radial bearing surfaces 114 for supporting the exciter shaft 110. As shown in Fig. As shown in Figure 4, the cylindrical areas which the bearing surfaces 114 provide for the support of the exciter shaft can have a smaller diameter than the cylindrical areas offset axially towards the recess 130 which the bearing surfaces 124 provide for the support of the counterweight. REFERENCE MARK LIST 100 vibration exciters 110 excitation wave 111 Exciter shaft rotation axis 112 Unbalanced rotary axis 113 Center of mass of the excitation wave 114 radial bearing surface for supporting the exciter shaft 115 attack 116 first stop surface 117 second stop surface 120 turnover weight 121 first direction of rotation, in particular rotation counterclockwise 122 second direction of rotation, in particular clockwise rotation 123 Center of gravity of the handling weight 124 radial bearing surface for storing the handling weight 130 recess E0 of the center of mass of the handling weight from the unbalance axis E1 first distance of the centers of mass of the excitation wave and the counterweight in the first position of the counterweight E2 second distance of the centers of mass of the excitation wave and the counterweight in the second position of the counterweight P1 first position of the turnover weight P2 second position of the turnover weight V r radial offset V x first offset V y second offset r radial direction x x-direction y y-direction QUOTES INCLUDED IN THE DESCRIPTION

[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0000] EP 2 881 516 A1

[0002] DE 10 2014 116 659 B4 [0002, 0003] US 4,830,534 A [0002, 0004] US 6,224,293 B1 [0002, 0005] EP 0 053 598 B1 [0002, 0006, 0008] EP 2 390 416 B1 [0002, 0007] OF 20 2016 103 865 U1 [0002, 0008] DE 10 2020 132 973 A1 [0002, 0009]

Claims

[1] Vibration exciter (100) for a soil compaction machine, comprising: - a balanced excitation shaft (110) with a stop (115) for a counterweight (120), wherein the excitation shaft (110) has an excitation shaft rotation axis (111) about which the excitation shaft (110) is rotatable, - the counterweight (120), which is arranged to rotate relative to the excitation shaft (110) about an unbalance axis of rotation (112), wherein the excitation shaft axis of rotation (111) is offset from the unbalance axis of rotation (112) by a radial offset (V) r ) is arranged in a staggered pattern. [2] Vibration exciter (100) according to claim 1, wherein the center of mass (113) of the exciter shaft (110) is located on the exciter shaft rotation axis (111). [3] Vibration exciter (100) according to one of the preceding claims, wherein the stop (115) is integrally formed with the excitation shaft (110). [4] Vibration exciter (100) according to one of the preceding claims, wherein in a first position (P1) of the counterweight (120) there is a first distance (E1) between the exciter shaft rotation axis (111) and the center of mass (123) of the counterweight (120), and wherein in a second position (P2) of the counterweight there is a second distance (E2) between the exciter shaft rotation axis (111) and the center of mass (123) of the counterweight (120), wherein the second distance (E2) differs from the first distance (E1). [5] Vibration exciter (100) according to claim 4, wherein when the exciter shaft (110) is rotated in a first direction of rotation (121) the counterweight (120) in the first position (P1) strikes a first stop surface (116) of the stop (115), and wherein when the exciter shaft (110) is rotated in an opposite second direction of rotation (122) the counterweight (120) in the second position (P2) strikes a second stop surface (117) of the stop (115). [6] Vibration exciter (100) according to claim 5, wherein the first stop surface (116) and the second stop surface (117) are arranged opposite each other, in particular wherein the first stop surface (116) and the second stop surface (117) are arranged substantially parallel to each other. [7] Vibration exciter (100) according to one of the preceding claims, wherein the stop (115) is provided by a first stop (115A) and a second stop (115B), wherein the second stop (115B) is axially spaced from the first stop (115A) along the exciter shaft rotation axis (111), and wherein the exciter shaft (110) has a recess (130) between the first stop (115A) and the second stop (115B). [8] Vibration exciter (100) according to one of the preceding claims, wherein the counterweight (120) surrounds the exciter shaft (110) in the circumferential direction to at least 25%, in particular to at least 30%, in particular to at least 40%. [9] Vibration exciter (100) according to one of the preceding claims, wherein the radial offset (V r ) in a range of 1 mm ≤ Vr ≤ 30 mm, in particular 5 mm ≤ Vr ≤ 15 mm. [10] Vibration exciter (100) according to one of the preceding claims, wherein the radial offset (V r ) by a first offset (V x ) and a second offset (V y ) is formed, with the second offset (V y ) perpendicular to the first offset (V x ) is. [11] Vibration exciter (100) according to claim 10, wherein the first offset (V x ) greater than, less than or equal to the second offset (V y ) is. [12] Vibration exciter (100) according to one of claims 10 or 11, wherein the first offset (V x ) lies in a range of 1 to 20 mm. [13] Vibration exciter (100) according to one of claims 10 to 12, wherein the second offset (V y ) lies in a range of 1 to 10 mm. [14] Use of one or more vibration exciters according to any of the preceding claims in a two-amplitude directional oscillator, a switchable oscillation bandage or a switchable circular exciter. [15] Soil compaction machine comprising at least one vibration exciter (100) according to one of the preceding claims.

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