EP2172279B1 - Device for generating a circuit vibration or a directed vibration with infinitely adjustable vibration amplitude or exciter power - Google Patents

Device for generating a circuit vibration or a directed vibration with infinitely adjustable vibration amplitude or exciter power Download PDF

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Publication number
EP2172279B1
EP2172279B1 EP09010928A EP09010928A EP2172279B1 EP 2172279 B1 EP2172279 B1 EP 2172279B1 EP 09010928 A EP09010928 A EP 09010928A EP 09010928 A EP09010928 A EP 09010928A EP 2172279 B1 EP2172279 B1 EP 2172279B1
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EP
European Patent Office
Prior art keywords
weights
imbalance
unbalanced weights
transmission means
vibration
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EP09010928A
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German (de)
French (fr)
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EP2172279A1 (en
Inventor
Hans-Werner Kürten
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Bomag GmbH and Co OHG
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Bomag GmbH and Co OHG
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/10—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
    • B06B1/16—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving rotary unbalanced masses
    • B06B1/161—Adjustable systems, i.e. where amplitude or direction of frequency of vibration can be varied
    • B06B1/166—Where the phase-angle of masses mounted on counter-rotating shafts can be varied, e.g. variation of the vibration phase
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18344—Unbalanced weights

Definitions

  • the invention relates to a device for generating a circular vibration or a directed vibration according to the preambles of the independent claims.
  • Such devices are used in particular for construction machines for soil compaction.
  • the fundamental waves are synchronously and in opposite directions, for example, by means of directly meshing spur gears in rotation.
  • the angular positions of the imbalance weights are changed so that the effective exciter force, which is composed of the centrifugal forces of individual imbalance weights, increases or decreases continuously within a predetermined range.
  • waves are used to adjust the oscillation amplitude or excitation force on which are on the one hand rotatably connected to the shaft and the other rotatably mounted on their imbalance weights.
  • the rotatably mounted imbalance weights usually adjusted only at standstill, in their positions relative to the rotationally fixed imbalance weights and locked.
  • Out DE 2736264 A1 is a vibration exciter with two mutually displaceable imbalance bodies known which also allows adjustment during operation.
  • a first unbalance body in a fork piece about a transverse axis is rotatably connected by means of a push rod with an axially displaceable on the axis of rotation slide for folding the unbalanced body.
  • Another unbalance body stands with the first imbalance body by means of a toothing in positive connection. If the slide is moved axially, then the two unbalance bodies rotate either to or from each other. In this way, the amplitude of the excitation force is varied.
  • the disadvantage is that in this case the axially displaceable slider and the push rod connection occupy a lot of space on the axis of rotation, so that a compact design of the vibration generator is impossible.
  • the invention is therefore based on the object to provide a device of the type mentioned, which overcomes the disadvantages of the known prior art.
  • the device according to the invention has imbalance weights which are rotatably mounted on the respective basic shaft on this.
  • a coupling which comprises a transmission means rotatably connected to the fundamental wave.
  • This transmission means is designed so that it acts as a driver on the imbalance weights on the one hand and on the other upon adjustment of the vibration amplitude of the excitation force causes an opposite rotation of the imbalance weights.
  • the transmission means of the coupling according to the invention essentially performs two functions. On the one hand, it serves as a driver for the adjacent unbalanced weights, so that these imbalance weights in normal operation, d. H. if a fixed setting for the vibration amplitude of the excitation force is selected, synchronize with the fundamental wave synchronously and in the same direction. In addition, with the desired change in the angular positions of the imbalance weights in order to change the amplitude of vibration of the excitation force during the running of the device, the transmission means effects an opposite rotation of the adjacent imbalance weights.
  • the device according to the invention should preferably serve to generate a circular oscillation by means of a shaft or a directed oscillation, that is, with at least two counter-rotating fundamental waves.
  • the coupling comprises a device with toothing parts, preferably with bevel gears, in particular with at least one pinion and two ring gears, wherein each an unbalanced weight has a ring gear and the transmission means is at least one pinion, which with the both wheels are engaged.
  • Ring gears / pinion pairings prove to be particularly suitable to meet the features indicated in the independent claims.
  • the coupling prefferably has a plurality of transmission means, each offset by a preferably identical angle.
  • two transmission means are used for reasons of symmetrical force distribution.
  • more than two transmission means can be used.
  • the transmission means are rotatably mounted on a transmission medium carrier and have an axis of rotation which intersects perpendicularly the axis of rotation of the fundamental shaft.
  • the functions of the transmission means namely the driver function and the function of the rotation reversal during adjustment, facilitated.
  • other designs are possible.
  • the fundamental shaft has at least one transverse bore for receiving the transmission medium carrier.
  • transmission means in particular bevel gears, and other parts.
  • means, in particular thrust bearings, for receiving centrifugal forces, which are generated by the transmission means are arranged on the transmission medium carrier. Thanks to the compact design of the transmission means, lower centrifugal forces are generated anyway than with conventional devices. Nevertheless, small axial ball bearings are suitable for absorbing centrifugal forces in order to further increase operational safety and ease of movement.
  • the transmission medium carriers it proves to be advantageous for the transmission medium carriers to be floatingly mounted on the transmission medium carrier. As a result, slight movements of the transmission means along the longitudinal axis of the transmission medium carrier are possible. As a result, the transmission medium carrier is protected from excessive stress due to bending moments and stresses.
  • Another basic idea of the invention is that only one of the imbalance weights is connected to an adjustment unit. It is thus possible to adjust with the adjustment of a single weight all arranged on the same fundamental unbalance weights exactly.
  • a further preferred embodiment of the invention provides that the fundamental wave has a plurality of imbalance weight pairs each having two imbalance weights and a coupling arranged between these imbalance weights. All imbalance weights can have the same size and mass. With the same mass of imbalance weights, the support moments cancel each other over the transmission medium carrier. As a result, the required supporting and adjusting forces are very low. Depending on the application, any number of imbalance weight pairs can be arranged on a basic shaft.
  • the imbalance weight pairs are thereby connected in series, that in each case adjacent imbalance weights of the imbalance weight pairs are connected in phase with each other.
  • phase equality is understood to mean that the angular positions of these imbalance weights are the same with respect to the fundamental. Consequently, phase difference is understood to mean the difference between the angular positions of the imbalance weights relative to one another.
  • the fundamental wave has an even number of imbalance weight pairs, which are connected in series. For example, if two, four or six imbalance weight pairs (ie four, six or eight imbalance weights with corresponding couplings) connected in series on a fundamental wave, so a tilting torque-free operation of the device is guaranteed, since the angular positions of the imbalance weights left and right with respect to the center of gravity the fundamental wave are symmetrical.
  • the imbalance weights of the device according to the invention on means for Axialspielverring ceremonies and reducing the backlash on.
  • These means may be, for example, spring elements.
  • the adjusting units of the two parallel fundamental waves are in operative connection.
  • the device according to the invention provides an oil pump for lubricating the teeth and the rolling bearing.
  • the efficient dosing by means of a sprinkler tube can reduce the oil level in the housing. This reduces the power loss due to the "splashing" of the imbalance weights in the oil bath.
  • the device according to the invention may comprise means for detecting the instantaneous positions of the imbalance weights, in particular sensors for detecting the relative phase difference of the imbalance weights to be adjusted. This also makes it possible to realize a frequency adjustment while maintaining a specific centrifugal force.
  • a great advantage of the invention is the high compactness. As a result, the device according to the invention can be installed without problems even in existing production machines with little effort.
  • FIG. 1 shows a first unbalanced weight pair 11 of the first fundamental wave 10 with the imbalance weights 12, 13.
  • the coupling 40 which has the two ring gears 43, 44 and the pinion 41, 42 designed as a transmission means 46.
  • the pinions 41, 42 are symmetrical with respect to the axis of rotation of the fundamental shaft 10, offset by 180 ° and arranged rotatably on the transmission medium carrier 45. Further, thrust bearings 48 can be seen, which serve to receive the centrifugal forces generated by the pinion 41, 42.
  • the adjusting unit 30 has an adjusting sleeve 31, which rotatably with the first imbalance weight 12 with an axial securing, z. B. via screws 36, is connected.
  • the inner wall of the adjusting sleeve 31 is provided with two offset by 180 ° coil grooves 32.
  • the adjusting pin 33 which is guided in a slot 39 in the basic shaft 10, engages in the helical grooves 32.
  • an axial movement of the adjusting piston 34 which is carried out in this embodiment by means of a single-acting hydraulic cylinder, leads to a rotating movement of Adjustment sleeve 31 and thus the imbalance weight 12.
  • Such adjusting units are for example off DE 2409417 A1 known. In the in Fig.
  • the ring gear 43 which is fixedly connected to the imbalance weight 12, rotates in the same direction as the imbalance weight 12 in the direction of arrow 102.
  • the pinion 41, 42 which are rotatably mounted on a transmission medium carrier 45 and with the ring gear 43 via the conical toothing in engagement are, wherein the transmission medium carrier 45 in a transverse bore 49 rotatably connected to the fundamental shaft 10 is rotated.
  • the rotation of the pinions 41, 42 takes place in indicated arrow directions 103, 104, ie in the clockwise direction, when the rotation is observed from the axial bearing 48 of the pinion 42 in the direction of the positive z-axis.
  • the rotation of the pinion 41, 42 causes the rotation of the ring gear 44 and thus also the imbalance weight 13.
  • a rotation of the imbalance weight 12, for example, by 90 ° relative to its starting position with respect to the imbalance shaft 10 causes a rotation of the imbalance weight 13 also by 90 °, but in the opposite direction of rotation, so that the imbalance weights 12, 13 rotate relative to or from each other by 180 °
  • the helical grooves 32 of the adjusting sleeve 31 are designed so that the adjusting sleeve 31 of a in Fig. 1 shown position (setting for minimum or no exciter force) to a in Fig. 3 shown position (setting for maximum excitation force) to exactly 90 ° is rotatable.
  • the imbalance weights can each rotate by 90 ° in opposite directions relative to a total of 180 °. Between the settings for minimum and maximum excitation force, any continuous adjustment is possible.
  • the rotation of the imbalance weights 12, 13 is usually in operation during rotation of the fundamental wave 10.
  • At a fixed phase difference of the imbalance weights 12, 13 are rotatably mounted by means of bearings 14, 15 imbalance weights 12 and 13 via the transmission means 46, in this case over the teeth with the pinions 41, 42 taken.
  • the sprockets stand still.
  • the connection via the toothing is thus to be regarded as a static connection.
  • the set imbalance weights 12, 13 rotate in the same direction with the fundamental.
  • a great advantage of the device according to the invention becomes clear.
  • the coupling 40 Due to the design of the coupling 40 by means of ring gears 43, 44 and pinion 41, 42, the inertia of the imbalance weights 12, 13 occurring during the rotation of the basic shaft 10 are mutually supported via the pinions 41, 42, so that no unwanted rotation of the imbalance weights 12, 13 may occur.
  • the coupling 40 together with the transmission means 46 favors a kind of self-locking. It also follows that due to the symmetrical engagement of the gearing parts with respect to the axis of symmetry of the transmission medium carrier 45, the transmission medium carriers 45 only have to absorb minimal supporting forces and supporting moments, so that great advantages in terms of service life and robustness of the coupling 40 according to the invention are achieved.
  • the teeth can be designed, for example, as forged or cast teeth parts easily and inexpensively.
  • the adjustment of the oscillation amplitude of the excitation force in operation by means of opposing rotation of the imbalance weights 12, 13 is a superposition of the partial movements "rotation of the imbalance weights 12, 13 with the rotational speed of the imbalance shaft 10" and "opposing rotation of the imbalance weights 12, 13 by a desired angular amount” consider.
  • FIG. 3 shows the device 1 according to the invention in a position in which the excitation force is a maximum, since the imbalance weights 12, 13 with respect to the fundamental shaft 10 have the same angular positions.
  • FIG. 4 shows a longitudinal section of the device according to the invention 1.
  • Each imbalance weight pair 11, 21 has a coupling 40 and 50, respectively.
  • the neighboring ones Unbalance weights 13, 22 of the imbalance weight pairs 11, 21 connected in phase by means of a positive connection element 19. This allows a series connection of the imbalance weight pairs 11, 21, so that only a single adjustment 30 must be connected to only a single imbalance weight 12 to allow simultaneous adjustment of all imbalance weights 12, 13, 22, 23 located on the imbalance shaft 10. All unbalance weights 12, 13, 22 23 are suitably the same size and the same weight.
  • the couplings 40 and 50 are the same.
  • the coupling 40 causes an opposite rotation of the imbalance weights 12, 13 by 90 °, so that the relative rotation of the imbalance weights 12, 13 is 180 ° in total.
  • the coupling 50 leads to an opposing rotation of the imbalance weight 23 in comparison to the imbalance weights 22, 13.
  • the internal imbalance weights 13, 22 are kept in phase by the series connection of imbalance weight pairs 11, 21 and in the opposite direction Direction rotate as the outer imbalance weights 12, 23, which in turn are held in phase by means of the couplings 40, 50 and the connecting element 19.
  • a great advantage in the arrangement of an even number of imbalance weight pairs 11, 21 connected in series on a basic shaft 10 is that the rolling bearings 28, 29 of the imbalance shaft 10, thanks to the approximately symmetrical design of the unbalanced shaft 10 with respect to the center of the imbalance shaft 10 not be burdened by undesirable "tilting moments".
  • FIG. 6 shows an overall perspective view of an embodiment of the invention.
  • a hydraulic drive 90 with the drive shaft 91 drives one of the two basic shafts 10 or 60 via spur gears (not shown here) directly.
  • the fundamental waves 10, 60 have the same constituents.
  • the modes of operation of both fundamental waves 10, 60 are also identical.
  • the spur gear 80 is connected via connecting elements, such. As screws / nut, fixed to the first imbalance weight 12th connected to the basic shaft 10 and thus also with the adjusting sleeve 31 of the adjusting unit 30.
  • the spur gear 81 is connected to the imbalance weight 62 of the basic shaft 60 and the adjusting sleeve of the adjusting unit 70.
  • the adjustment of the imbalance weights 12, 13, 22, 23 of the basic shaft 10 with the adjustment movement of the imbalance weights 62, 63, 65, 66 of the basic shaft 60 can be synchronized via the pair of spur gears and reversed in rotation.
  • the hydraulic actuators 37 of both adjusting units 30, 70 can be combined in such a way that only single-acting hydraulic cylinders can be used instead of the double-acting ones. If, for example, the adjusting pin 33 of the adjusting unit 30 in the positive x-direction ( Fig. 4 ) is "pressed in”, it is on the opposite synchronization by means of the spur gears 80, 81 of the adjusting pin (not shown here) of the adjusting unit 70 "pushed out” accordingly in the negative x-direction.
  • the oscillation amplitude of the excitation force can be adjusted easily and quickly by the rotation of the imbalance weights from a minimum value, ie 0 kN to a maximum value, for example 174 kN, continuously and during the rotation of the shaft. It has proven to be particularly advantageous that the imbalance weights 12, 13, 22, 23 and 62, 63, 65, 66 in operation until reaching the rated speed of the fundamental waves 10, 60 in the in Fig. 1 . 4 or 6 remain shown angular positions. At these angular positions no directional vibration is generated. After reaching the rated speed, the imbalance weights can be rotated until a desired amount of vibration amplitude of the exciter force is reached. This allows a "soft" start.
  • the drive motor of the device 1 according to the invention for example a diesel engine, can be operated constantly at rated speed and only the adjustment of the excitation force exerts an influence on engine operation, the drive motor can be operated efficiently and with optimized fuel consumption.
  • the starting behavior is better overall.
  • the imbalance weights are first rotated at rated speed in the "zero position" so that no excitation forces are generated and then turned off the machine or reversed. Due to the constant operation of the device according to the invention at rated speed undesirable resonance ranges are avoided. As a result, no "tumbling" of the rolling body occurs. If the device according to the invention is used for ground-compacting machines, unwanted transverse grooves, for example, can be avoided so that overall the quality of compaction can be improved. The possibility of quick and convenient adaptation of the excitation force to the local conditions also contributes to the improvement. Due to the compactness can the device 1 according to the invention also incorporate easily into existing series machines. By adjusting the compaction performance to the ground noise reduction for both the environment and for the driver is achieved. Furthermore, the vibration load of the machine structure is significantly reduced.
  • FIGS. 7 to 9 show a further preferred embodiment of the invention.
  • the two adjacent imbalance weights 13, 22 of the imbalance weight pairs 11 and 21 are not connected in phase and fixed to each other, but by means of an additional coupling 150, which essentially corresponds to the couplings 40, 50, arranged rotatable against each other.
  • the second fundamental wave 60 has an imbalance weight 160, which is arranged rotationally fixed on the second fundamental wave 60.
  • FIG. 7 shows an adjustment of the imbalance weights 12, 13, 22, 23 for the "straight ahead" in the indicated arrow direction 170.
  • the imbalance weights 12, 23 in the yz plane occupy an angle of + 45 ° with respect to the positive z-axis.
  • the imbalance weights 13, 22 have an angle of -45 ° with respect to the z-axis.
  • a horizontal component is generated in addition to the vertical component of the excitation force, whereby the device in the running direction shown, namely in the positive y-axis, moves straight ahead.
  • the amount of the horizontal component is adjustable in a range, so that the travel speed can be optimally adjusted. If the device is used for a vibrating plate, then no separate drive for the forward or backward movement of the vibrating plate is necessary.
  • FIG. 8 shows an adjustment of the imbalance weights 12, 13, 22, 23 for the "turning to the left" in the indicated direction of arrow 180.
  • the first imbalance weight 12 via the known adjusting device 30 which is fixedly connected to the imbalance weight 12, starting from the in Fig. 7 shown angular position rotated by - 45 ° with respect to the positive z-axis, so that the unbalance force of the imbalance weight 12 parallel to the z-axis in the direction of the positive z-axis.
  • the coupling 40 causes an opposite rotation of the imbalance weight 13 with respect to the imbalance weight 12, so that the imbalance weights 12, 13 are in phase.
  • the couplings 150, 50 each lead to the opposite rotation of the adjacent Imbalance weights 13, 22 and 22, 23, so that the imbalance weights in Fig.
  • FIG. 9 shows an adjustment of the imbalance weights 12, 13, 22, 23 for the "cornering to the right" in the indicated arrow direction 190.
  • the first imbalance weight 12 via the known adjusting device 30 which is fixedly connected to the imbalance weight 12, starting from the in Fig. 7 shown angular position rotated by + 45 ° with respect to the positive z-axis, so that the unbalance force of the imbalance weight 12 shows parallel to the y-axis in the direction of the positive y-axis.
  • the imbalance weight 22 is rotated by + 45 ° due to the coupling 150, ie in the same direction of rotation as the imbalance weight 12.
  • the coupling 50 leads to a rotation of the imbalance weight 23 by - 45 °.
  • Fig. 8 shown setting the force vectors of the "left" imbalance weight pair 21 with the imbalance weights 22, 23 are rectified and the force vectors of the "right” imbalance weight pair 11 with the imbalance weights 12, 13 directed against.
  • the cornering to the right during operation ie in the direction of the negative x-axis, allows.
  • example according to the invention can be realized in a simple and compact manner a traveling and steerable machine, in particular vibration plate for soil compaction, the driving speed and the amplitude of the excitation force can be optimally adjusted as needed.
  • FIG. 10 shows a particularly compact and simple embodiment of the device according to the invention.
  • the first basic shaft 10 comprises only one imbalance weight pair 11 with the rotatably mounted imbalance weights 12, 13 and a coupling 40 arranged between the imbalance weights 12, 13 and an adjusting device 30 which is connected to the first imbalance weight 12.
  • a second fundamental wave 60 is positively coupled, wherein the second imbalance shaft has a non-rotatably mounted on it imbalance weight 160.
  • the adjustment of the angular positions of the imbalance weights 12, 13 takes place in the manner described above according to the invention.

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Abstract

The circuit exciter has a coupling provided between unbalanced weights (12, 13) that are rotatably supported on a primary shaft (10). The coupling includes a transmission unit connected with the primary shaft in a rotationally fixed manner and designed such that the transmission unit acts as an actuator on the weights and causes an adjustment of vibration amplitude of exciter force by the rotation of the weights in an opposite direction. The weights are relatively rotated to-or from each other between minimum and maximum values.

Description

Die Erfindung betrifft eine Vorrichtung zur Erzeugung einer Kreisschwingung oder einer gerichteten Schwingung nach den Oberbegriffen der unabhängigen Ansprüche. Solche Vorrichtungen kommen insbesondere bei Baumaschinen zur Bodenverdichtung zum Einsatz. Es werden gewöhnlich zwei parallel im gleichen Gehäuse angeordnete Grundwellen verwendet, auf denen sich jeweils Unwuchtgewichte befinden. Zur Erzeugung einer gerichteten Schwingung werden die Grundwellen synchron und gegensinnig beispielsweise mittels direkt kämmender Stirnräder in Rotation versetzt. Zur stufenlosen Verstellung der Schwingungsamplitude der Erregerkraft werden die Winkelstellungen der Unwuchtgewichte so geändert, dass die wirksame Erregerkraft, die sich aus den Fliehkräften einzelner Unwuchtgewichte zusammensetzt, stufenlos innerhalb eines vorgegebenen Bereichs zu- oder abnimmt.The invention relates to a device for generating a circular vibration or a directed vibration according to the preambles of the independent claims. Such devices are used in particular for construction machines for soil compaction. There are usually used two parallel in the same housing arranged fundamental waves, on each of which imbalance weights are. To generate a directional vibration, the fundamental waves are synchronously and in opposite directions, for example, by means of directly meshing spur gears in rotation. For stepless adjustment of the oscillation amplitude of the excitation force, the angular positions of the imbalance weights are changed so that the effective exciter force, which is composed of the centrifugal forces of individual imbalance weights, increases or decreases continuously within a predetermined range.

Herkömmlich werden zur Verstellung der Schwingungsamplitude bzw. Erregerkraft Wellen verwendet, auf denen sich zum einen drehfest mit der Welle verbundene und zum anderen drehbar auf ihr gelagerte Unwuchtgewichte befinden. Zur Verstellung der Winkelstellung werden die drehbar gelagerten Unwuchtgewichte, meist nur im Stillstand, in ihren Positionen gegenüber den drehfesten Unwuchtgewichten verstellt und arretiert.Conventionally, waves are used to adjust the oscillation amplitude or excitation force on which are on the one hand rotatably connected to the shaft and the other rotatably mounted on their imbalance weights. To adjust the angular position, the rotatably mounted imbalance weights, usually adjusted only at standstill, in their positions relative to the rotationally fixed imbalance weights and locked.

Aus DE 2736264 A1 ist ein Schwingungserreger mit zwei gegeneinander verschiebbaren Unwuchtkörpern bekannt, welcher auch eine Verstellung während des Betriebes ermöglicht. Dazu ist ein erster Unwuchtkörper in einem Gabelstück um eine Querachse drehbar mittels einer Schubstange mit einem axial auf der Rotationsachse verschiebbaren Schieber zum Umlegen des Unwuchtkörpers verbunden. Ein weiterer Unwuchtkörper steht mit dem ersten Unwuchtkörper mittels einer Verzahnung in formschlüssiger Verbindung. Wird der Schieber axial bewegt, so verdrehen sich die beiden Unwuchtkörper entweder zu- oder voneinander. Auf diese Weise wird die Amplitude der Erregerkraft variiert. Nachteilig allerdings ist, dass hierbei der axial verschiebbare Schieber und die Schubstangenverbindung sehr viel Platz auf der Rotationsachse einnehmen, so dass eine kompakte Bausweise des Schwingungserregers unmöglich ist.Out DE 2736264 A1 is a vibration exciter with two mutually displaceable imbalance bodies known which also allows adjustment during operation. For this purpose, a first unbalance body in a fork piece about a transverse axis is rotatably connected by means of a push rod with an axially displaceable on the axis of rotation slide for folding the unbalanced body. Another unbalance body stands with the first imbalance body by means of a toothing in positive connection. If the slide is moved axially, then the two unbalance bodies rotate either to or from each other. In this way, the amplitude of the excitation force is varied. The disadvantage, however, is that in this case the axially displaceable slider and the push rod connection occupy a lot of space on the axis of rotation, so that a compact design of the vibration generator is impossible.

Ferner besteht der Nachteil darin, dass bei dem Schwingungserreger gemäß DE 2736264 A1 bezüglich der Anordnung von Unwuchtkörpern kein Spielraum gegeben ist, da nur immer zwei Unwuchtkörper pro Rotationswelle angeordnet werden können. Wenn man beispielsweise zwei weitere Unwuchtkörper auf der gleichen Rotationsachse anordnen wollte, müsste ein weiterer Schieber mit einer weiteren Schubstange auf der anderen Stirnseite der Welle angeordnet werden, wodurch der Bauraum noch weiter vergrößert werden würde. Ferner stellt die Schubstange als Verbindungsteil zum Verstellelement ein empfindliches Bauteil dar. Außerdem ist aufgrund der asymmetrischen Anordnung der Schubstange und aufgrund der Form der Unwuchtköper selbst bei komplett umgelegten Unwuchtkörpern keine "Nulleinstellung" der Erregerkraft möglich, so dass die Maschine ständig eine Unwucht und somit eine gerichtete Schwingung erzeugt, solange sich die Welle dreht. Ein Schwingungserreger mit zwei gegen einander verschiebbaren umwuchtgewichten, welcher ebenfalls eine verstellung während des Betriebes ermöglicht ist aus US 4 850 821 bekannt.Furthermore, the disadvantage is that in the vibration exciter according to DE 2736264 A1 no margin is given with respect to the arrangement of unbalanced bodies, since only two unbalanced bodies per rotation shaft can be arranged. For example, if you wanted to arrange two more unbalanced body on the same axis of rotation, another slide would have to be arranged with a further push rod on the other end of the shaft, whereby the space would be further increased. In addition, due to the asymmetric arrangement of the push rod and due to the shape of the unbalanced body even with completely folded unbalanced bodies no "zero adjustment" of the excitation force is possible, so that the machine constantly an imbalance and thus a directed vibration generated as long as the shaft rotates. A vibration exciter with two counterbalanced balancing weights, which also allows an adjustment during operation is made US 4,850,821 known.

Der Erfindung liegt daher die Aufgabe zugrunde, eine Vorrichtung der eingangs genannten Art anzugeben, die die Nachteile des bekannten Standes der Technik überwindet. Insbesondere ist es die Aufgabe der Erfindung, eine sehr kompakte Bauweise für eine Vorrichtung zur Erzeugung einer Kreisschwingung oder einer gerichteten Schwingung zu ermöglichen, wobei die Schwingungsamplitude der Erregerkraft zuverlässig und bequem zwischen einem minimalen Wert, welcher Null sein kann aber nicht sein muss, und einem maximalen Wert stufenlos verstellbar ist. Zusätzlich ist es Aufgabe der Erfindung, eine Vorrichtung anzugeben, bei der eine modulare Erweiterung der Grundwelle mit zusätzlichen Unwuchtgewichten einfach, kostengünstig und ebenfalls kompakt möglich ist.The invention is therefore based on the object to provide a device of the type mentioned, which overcomes the disadvantages of the known prior art. In particular, it is the object of the invention to enable a very compact construction for a device for generating a circular oscillation or a directed oscillation, wherein the oscillation amplitude of the excitation force reliably and conveniently between a minimum value, which may be zero but not must, and a maximum value is infinitely adjustable. In addition, it is an object of the invention to provide a device in which a modular extension of the fundamental wave with additional imbalance weights simple, inexpensive and also compact is possible.

Die Aufgabe der Erfindung wird gelöst durch den Gegenstand der unabhängigen Ansprüche. Die abhängigen Ansprüche sind auf vorteilhafte Ausführungsformen der Erfindung gerichtet.The object of the invention is achieved by the subject matter of the independent claims. The dependent claims are directed to advantageous embodiments of the invention.

Die erfindungsgemäße Vorrichtung weist Unwuchtgewichte auf, die um die jeweilige Grundwelle drehbar auf dieser gelagert sind. Zudem weist sie eine Kopplung auf, welche ein mit der Grundwelle drehfest verbundenes Übertragungsmittel umfasst. Dieses Übertragungsmittel ist so beschaffen, dass es zum einen als Mitnehmer auf die Unwuchtgewichte wirkt und zum anderen bei Verstellung der Schwingungsamplitude der Erregerkraft eine gegensinnige Verdrehung der Unwuchtgewichte bewirkt.The device according to the invention has imbalance weights which are rotatably mounted on the respective basic shaft on this. In addition, it has a coupling, which comprises a transmission means rotatably connected to the fundamental wave. This transmission means is designed so that it acts as a driver on the imbalance weights on the one hand and on the other upon adjustment of the vibration amplitude of the excitation force causes an opposite rotation of the imbalance weights.

Das Übertragungsmittel der Kopplung gemäß der Erfindung übernimmt im Wesentlichen zwei Funktionen. Zum einen dient es als Mitnehmer für die benachbart angeordneten Unwuchtgewichte, so dass diese Unwuchtgewichte im Normalbetrieb, d. h. wenn eine feste Einstellung für die Schwingungsamplitude der Erregerkraft gewählt ist, mit der Grundwelle synchron und gleichsinnig rotieren. Zusätzlich bewirkt das Übertragungsmittel bei gewünschter Änderung der Winkelstellungen der Unwuchtgewichte, um die Schwingungsamplitude der Erregerkraft während des Laufes der Vorrichtung zu ändern, eine gegensinnige Verdrehung der benachbarten Unwuchtgewichte.The transmission means of the coupling according to the invention essentially performs two functions. On the one hand, it serves as a driver for the adjacent unbalanced weights, so that these imbalance weights in normal operation, d. H. if a fixed setting for the vibration amplitude of the excitation force is selected, synchronize with the fundamental wave synchronously and in the same direction. In addition, with the desired change in the angular positions of the imbalance weights in order to change the amplitude of vibration of the excitation force during the running of the device, the transmission means effects an opposite rotation of the adjacent imbalance weights.

Mit der erfindungsgemäßen Vorrichtung werden unter anderem große Vorteile hinsichtlich der Kompaktheit der gesamten Vorrichtung, Robustheit der Kopplung sowie einfacher und schneller Verstellungsmöglichkeit erzielt. Ferner können Herstellungskosten dank der Verwendung einfacher und gleicher Bauteile reduziert werden. Die erfindungsgemäße Vorrichtung soll vorzugsweise zur Erzeugung einer Kreisschwingung mittels einer Welle oder einer gerichteten Schwingung, also mit mindestens zwei gegensinnig rotierenden Grundwellen, dienen.With the device according to the invention, among other things, great advantages are achieved with regard to the compactness of the entire device, robustness of the coupling as well as easy and quick adjustment. Furthermore, manufacturing costs can be reduced thanks to the use of simple and identical components. The device according to the invention should preferably serve to generate a circular oscillation by means of a shaft or a directed oscillation, that is, with at least two counter-rotating fundamental waves.

Eine vorteilhafte Ausgestaltung der Erfindung besteht darin, dass die Kopplung eine Vorrichtung mit Verzahnungsteilen, vorzugsweise mit Kegelrädern, insbesondere mit mindestens einem Ritzel und zwei Tellerrädern, umfasst, wobei jeweils ein Unwuchtgewicht ein Tellerrad aufweist und das Übertragungsmittel das mindestens eine Ritzel ist, welches mit den beiden Tellerrädern im Eingriff steht. Tellerräder/Ritzel-Paarungen erweisen sich als besonders geeignet, um die in den unabhängigen Ansprüchen gekennzeichneten Merkmale zu erfüllen.An advantageous embodiment of the invention is that the coupling comprises a device with toothing parts, preferably with bevel gears, in particular with at least one pinion and two ring gears, wherein each an unbalanced weight has a ring gear and the transmission means is at least one pinion, which with the both wheels are engaged. Ring gears / pinion pairings prove to be particularly suitable to meet the features indicated in the independent claims.

Es ist besonders zweckmäßig, dass die Kopplung mehrere jeweils um einen vorzugsweise gleichen Winkel versetzt angeordnete Übertragungsmittel aufweist. Vorzugsweise werden aus Gründen der symmetrischen Kraftverteilung zwei Übertragungsmittel verwendet. Allerdings können je nach Anwendungsfall auch mehr als zwei Übertragungsmittel eingesetzt werden.It is particularly expedient for the coupling to have a plurality of transmission means, each offset by a preferably identical angle. Preferably, two transmission means are used for reasons of symmetrical force distribution. However, depending on the application, more than two transmission means can be used.

Bevorzugt sind die Übertragungsmittel drehbar auf einem Übertragungsmittelträger angeordnet und weisen eine Rotationsachse auf, welche die Rotationsachse der Grundwelle senkrecht schneidet. Durch diese Bedingung werden die Funktionen des Übertragungsmittels, nämlich die Mitnehmer-Funktion und die Funktion der Drehsinnumkehr bei Verstellung, erleichtert. Es sind jedoch auch andere Ausführungen möglich.Preferably, the transmission means are rotatably mounted on a transmission medium carrier and have an axis of rotation which intersects perpendicularly the axis of rotation of the fundamental shaft. By this condition, the functions of the transmission means, namely the driver function and the function of the rotation reversal during adjustment, facilitated. However, other designs are possible.

Vorzugsweise weist die Grundwelle mindestens eine Querbohrung zur Aufnahme des Übertragungsmittelträgers auf. Mittels der Querbohrung kann der Übertragungsmittelträger durch die Grundwelle durchgesteckt werden und anschließend von beiden Seiten mit Übertragungsmittel, insbesondere Kegelräder, und weiteren Teilen bestückt werden.Preferably, the fundamental shaft has at least one transverse bore for receiving the transmission medium carrier. By means of the transverse bore of the transmission medium carrier can be pushed through the basic shaft and then be equipped from both sides with transmission means, in particular bevel gears, and other parts.

Gemäß einer bevorzugten Ausführungsform sind auf dem Übertragungsmittelträger Mittel, insbesondere Axiallager, zur Aufnahme von Fliehkräften angeordnet, die durch das Übertragungsmittel erzeugt werden. Es werden dank der kompakten Ausführung der Übertragungsmittel ohnehin geringere Fliehkräfte erzeugt als bei herkömmlichen Vorrichtungen. Dennoch bieten sich kleine Axialkugellager zur Aufnahme von Fliehkräften an, um die Betriebssicherheit und Leichtgängigkeit noch weiter zu erhöhen.According to a preferred embodiment, means, in particular thrust bearings, for receiving centrifugal forces, which are generated by the transmission means, are arranged on the transmission medium carrier. Thanks to the compact design of the transmission means, lower centrifugal forces are generated anyway than with conventional devices. Nevertheless, small axial ball bearings are suitable for absorbing centrifugal forces in order to further increase operational safety and ease of movement.

Es erweist sich als vorteilhaft, dass die Übertragungsmittelträger schwimmend auf dem Übertragungsmittelträger gelagert sind. Dadurch sind geringfügige Bewegungen der Übertragungsmittel entlang der Längsachse des Übertragungsmittelträgers möglich. Dadurch wird der Übertragungsmittelträger vor zu großer Belastung infolge von Biegemomenten und Spannungen bewahrt.It proves to be advantageous for the transmission medium carriers to be floatingly mounted on the transmission medium carrier. As a result, slight movements of the transmission means along the longitudinal axis of the transmission medium carrier are possible. As a result, the transmission medium carrier is protected from excessive stress due to bending moments and stresses.

Ein weiterer Grundgedanke der Erfindung liegt darin, dass nur eines der Unwuchtgewichte mit einer Verstelleinheit verbunden ist. Es ist also möglich, mit der Verstellung eines einzigen Gewichtes alle auf der gleichen Grundwelle angeordneten Unwuchtgewichte exakt zu verstellen.Another basic idea of the invention is that only one of the imbalance weights is connected to an adjustment unit. It is thus possible to adjust with the adjustment of a single weight all arranged on the same fundamental unbalance weights exactly.

Eine weitere bevorzugte Ausführungsvariante der Erfindung sieht vor, dass die Grundwelle mehrere Unwuchtgewichtspaare mit jeweils zwei Unwuchtgewichten und einer zwischen diesen Unwuchtgewichten angeordneten Kopplung aufweist. Dabei können sämtliche Unwuchtgewichte gleiche Größe und Masse besitzen. Bei gleicher Masse der Unwuchtgewichte heben sich die Stützmomente über den Übertragungsmittelträger gegenseitig auf. Hierdurch sind die erforderlichen Stütz- und Verstellkräfte sehr gering. Es können je nach Anwendungsfall beliebig viele Unwuchtgewichtpaare auf einer Grundwelle angeordnet werden.A further preferred embodiment of the invention provides that the fundamental wave has a plurality of imbalance weight pairs each having two imbalance weights and a coupling arranged between these imbalance weights. All imbalance weights can have the same size and mass. With the same mass of imbalance weights, the support moments cancel each other over the transmission medium carrier. As a result, the required supporting and adjusting forces are very low. Depending on the application, any number of imbalance weight pairs can be arranged on a basic shaft.

In einer besonders bevorzugten Ausführungsvariante werden die Unwuchtgewichtspaare dadurch in Serie geschaltet, dass jeweils benachbarte Unwuchtgewichte der Unwuchtgewichtspaare phasengleich miteinander verbunden werden. In diesem Zusammenhang wird unter Phasengleichheit verstanden, dass die Winkelstellungen dieser Unwuchtgewichte bezüglich der Grundwelle gleich sind. Folglich wird unter Phasendifferenz der Unterschied der Winkelstellungen der Unwuchtgewichte zueinander verstanden.In a particularly preferred embodiment, the imbalance weight pairs are thereby connected in series, that in each case adjacent imbalance weights of the imbalance weight pairs are connected in phase with each other. In this context, phase equality is understood to mean that the angular positions of these imbalance weights are the same with respect to the fundamental. Consequently, phase difference is understood to mean the difference between the angular positions of the imbalance weights relative to one another.

Dabei ist es besonders vorteilhaft, wenn die Grundwelle eine gerade Anzahl von Unwuchtgewichtspaaren aufweist, die in Serie geschaltet sind. Werden beispielsweise zwei, vier oder sechs Unwuchtgewichtpaare (also vier, sechs oder acht Unwuchtgewichte mit entsprechenden Kopplungen) auf einer Grundwelle in Serie geschaltet, so wird immer ein kippmomentfreies Betreiben der Vorrichtung gewährleistet, da die Winkelstellungen der Unwuchtgewichte links und rechts in Bezug auf den Schwerpunkt der Grundwelle symmetrisch sind.It is particularly advantageous if the fundamental wave has an even number of imbalance weight pairs, which are connected in series. For example, if two, four or six imbalance weight pairs (ie four, six or eight imbalance weights with corresponding couplings) connected in series on a fundamental wave, so a tilting torque-free operation of the device is guaranteed, since the angular positions of the imbalance weights left and right with respect to the center of gravity the fundamental wave are symmetrical.

Vorzugweise weisen die Unwuchtgewichte der erfindungsgemäßen Vorrichtung Mittel zur Axialspielverringerung und Verringerung des Zahnflankenspiels auf. Diese Mittel können beispielsweise Federelemente sein.Preferably, the imbalance weights of the device according to the invention on means for Axialspielverringerung and reducing the backlash on. These means may be, for example, spring elements.

Gemäß einer weiteren Ausführungsform der Erfindung sind die Verstelleinheiten der beiden parallelen Grundwellen in Wirkverbindung. Dadurch dass die Verstellhülsen der Verstelleinheiten beispielsweise über direkt kämmende Stirnräder miteinander synchronisiert und gegensinnig verdrehbar verbunden sind, können z. B. bei hydraulischen Verstelleinheiten statt der doppelt wirkenden Zylinder auch einfach wirkende jeweils für eine Welle verwendet werden.According to a further embodiment of the invention, the adjusting units of the two parallel fundamental waves are in operative connection. The fact that the adjusting sleeves of the adjusting units are synchronized with each other for example via directly meshing spur gears and rotatably connected in opposite directions, z. B. in hydraulic adjustment units instead of the double-acting cylinder and single-acting are used in each case for a shaft.

Vorzugsweise sieht die erfindungsgemäße Vorrichtung eine Ölpumpe zur Schmierung der Verzahnungen und der Wälzlager vor. Durch die effiziente Dosierung mittels eines Berieselungsrohres kann das Ölniveau im Gehäuse reduziert werden. Dadurch wird der Leistungsverlust aufgrund des "Planschens" der Unwuchtgewichte im Ölbad verringert.Preferably, the device according to the invention provides an oil pump for lubricating the teeth and the rolling bearing. The efficient dosing by means of a sprinkler tube can reduce the oil level in the housing. This reduces the power loss due to the "splashing" of the imbalance weights in the oil bath.

Es ist weiterhin vorteilhaft, die erfindungsgemäße Vorrichtung mittels eines außerhalb des Gehäuses befindlichen Schwenkantriebes verschwenkbar auszuführen. Hierdurch kann bei Bedarf der Wirkwinkel der erfindungsgemäßen Vorrichtung angepasst werden.It is also advantageous to perform the device according to the invention by means of a pivot drive located outside of the housing pivotable. In this way, if necessary, the effective angle of the device according to the invention can be adjusted.

Zusätzlich kann die erfindungsgemäße Vorrichtung Mittel zur Erfassung der momentanen Positionen der Unwuchtgewichte, insbesondere Sensoren zur Erfassung des relativen Phasenunterschieds der zu verstellenden Unwuchtgewichte aufweisen. Hierdurch ist es auch möglich, eine Frequenzverstellung unter Beibehaltung einer bestimmten Fliehkraft zu realisieren.In addition, the device according to the invention may comprise means for detecting the instantaneous positions of the imbalance weights, in particular sensors for detecting the relative phase difference of the imbalance weights to be adjusted. This also makes it possible to realize a frequency adjustment while maintaining a specific centrifugal force.

Ein großer Vorteil der Erfindung besteht in der hohen Kompaktheit. Dadurch lässt sich die erfindungsgemäße Vorrichtung problemlos nur mit geringem Aufwand auch in bereits bestehende Serienmaschinen einbauen.A great advantage of the invention is the high compactness. As a result, the device according to the invention can be installed without problems even in existing production machines with little effort.

Nachfolgend wird die Erfindung anhand von Zeichnungen weiter erläutert. Es zeigen schematisch

Fig. 1
eine perspektivische Teilansicht der erfindungsgemäßen Vorrichtung mit teilweise ge- schnittener Verstellhülse in Ausgangsstellung;
Fig. 2
eine perspektivische Teilansicht wie Fig. 1, jedoch um einen Winkel verstellt;
Fig. 3
eine perspektivische Teilansicht wie Fig. 1, jedoch um 180° verstellt;
Fig. 4
einen Längsschnitt durch die erfindungsgemäße Vorrichtung;
Fig. 5
einen Längsschnitt wie Fig. 4, jedoch die Unwuchtgewichte um 180° verstellt;
Fig. 6
eine perspektivische Gesamtansicht der erfindungsgemäßen Vorrichtung;
Fig. 7
eine perspektivische Ansicht einer weiteren Ausführungsvariante der Erfindung;
Fig. 8
eine perspektivische Ansicht wie Fig. 8, jedoch um - 45° verstellt;
Fig. 9
eine perspektivische Ansicht wie Fig. 8, jedoch um + 45° verstellt;
Fig. 10
eine perspektivische Ansicht einer weiteren Ausführungsvariante der Erfindung.
The invention will be further explained with reference to drawings. It show schematically
Fig. 1
a partial perspective view of the device according to the invention with partially cut adjusting sleeve in the initial position;
Fig. 2
a partial perspective view like Fig. 1 , but adjusted by an angle;
Fig. 3
a partial perspective view like Fig. 1 , but adjusted by 180 °;
Fig. 4
a longitudinal section through the device according to the invention;
Fig. 5
a longitudinal section like Fig. 4 , but the imbalance weights adjusted by 180 °;
Fig. 6
an overall perspective view of the device according to the invention;
Fig. 7
a perspective view of another embodiment of the invention;
Fig. 8
a perspective view like Fig. 8 , but adjusted by - 45 °;
Fig. 9
a perspective view like Fig. 8 , but adjusted by + 45 °;
Fig. 10
a perspective view of another embodiment of the invention.

Figur 1 zeigt ein erstes Unwuchtgewichtpaar 11 der ersten Grundwelle 10 mit den Unwuchtgewichten 12, 13. Zwischen den Unwuchtgewichten 12, 13 befindet sich die Kopplung 40, welche die beiden Tellerräder 43, 44 sowie die als Ritzel 41, 42 ausgeführte Übertragungsmittel 46 aufweist. Die Ritzel 41, 42 sind symmetrisch in Bezug auf die Rotationsachse der Grundwelle 10, um 180° versetzt und drehbar auf dem Übertragungsmittelträger 45 angeordnet. Ferner sind Axiallager 48 erkennbar, die zur Aufnahme der durch die Ritzel 41, 42 erzeugten Fliehkräfte dienen. FIG. 1 shows a first unbalanced weight pair 11 of the first fundamental wave 10 with the imbalance weights 12, 13. Between the imbalance weights 12, 13 is the coupling 40, which has the two ring gears 43, 44 and the pinion 41, 42 designed as a transmission means 46. The pinions 41, 42 are symmetrical with respect to the axis of rotation of the fundamental shaft 10, offset by 180 ° and arranged rotatably on the transmission medium carrier 45. Further, thrust bearings 48 can be seen, which serve to receive the centrifugal forces generated by the pinion 41, 42.

Die Verstelleinheit 30 weist eine Verstellhülse 31 auf, welche mit dem ersten Unwuchtgewicht 12 drehfest mit einer Axialsicherung, z. B. über Schrauben 36, verbunden ist. Die innere Wandung der Verstellhülse 31 ist mit zwei um 180° versetzt angeordneten Wendelnuten 32 versehen. Der Verstellstift 33, der in einem Langloch 39 in der Grundwelle 10 geführt ist, greift in die Wendelnuten 32. Somit führt eine axiale Bewegung des Verstellkolbens 34, welche bei diesem Ausführungsbeispiel mittels eines einfach wirkenden Hydraulik-Zylinders ausgeführt wird, zu einer rotierenden Bewegung der Verstellhülse 31 und somit des Unwuchtgewichtes 12. Solche Verstelleinheiten sind beispielsweise aus DE 2409417 A1 bekannt. In der in Fig. 1 gezeigten Winkelstellungen der Unwuchtgewichte 12, 13 ist das Unwuchtgewicht 13 gegenüber dem Unwuchtgewicht 12 genau um 180° verdreht. Bei einer Rotation der Grundwelle 10 in der gezeigten Stellung heben sich die Fliehkraftkomponenten der Unwuchtgewichte gegenseitig auf, so dass keine Erregerkraft auftritt.The adjusting unit 30 has an adjusting sleeve 31, which rotatably with the first imbalance weight 12 with an axial securing, z. B. via screws 36, is connected. The inner wall of the adjusting sleeve 31 is provided with two offset by 180 ° coil grooves 32. The adjusting pin 33, which is guided in a slot 39 in the basic shaft 10, engages in the helical grooves 32. Thus, an axial movement of the adjusting piston 34, which is carried out in this embodiment by means of a single-acting hydraulic cylinder, leads to a rotating movement of Adjustment sleeve 31 and thus the imbalance weight 12. Such adjusting units are for example off DE 2409417 A1 known. In the in Fig. 1 shown angular positions of the imbalance weights 12, 13, the imbalance weight 13 relative to the imbalance weight 12 is rotated exactly 180 °. Upon rotation of the fundamental shaft 10 in the position shown, the centrifugal components of the imbalance weights cancel each other, so that no excitation force occurs.

Anhand von Fig. 1, 2 und 3 wird die erfindungsgemäße Verstellung der Unwuchtgewichte 12, 13 genauer beschrieben. Hierzu wird zunächst nur die reine Verstellbewegung beschrieben, d. h. in diesem Fall wird zum besseren Verständnis angenommen, dass die Grundwelle 10 steht. Wird auf den Verstellkolben 34 Druck ausgeübt, so bewegt sich der mit dem Verstellkolben 34 verbundene Verstellstift 33 axial in Richtung positiver x-Achse, also in die angezeigte Pfeilrichtung 100. Dadurch verdreht sich die Verstellhülse samt dem damit verbundenen Unwuchtgewicht 12 in die Pfeilrichtung 101 und 102, also gegen den Uhrzeigersinn um die x-Achse, wenn man diese Drehung vom Stößel 35 aus in Richtung positiver x-Achse betrachtet.Based on Fig. 1 . 2 and 3 the adjustment of the imbalance weights 12, 13 according to the invention will be described in more detail. For this purpose, initially only the pure adjustment movement is described, ie in this case it is assumed for a better understanding that the fundamental shaft 10 is stationary. If pressure is exerted on the adjusting piston 34, the adjusting pin 33 connected to the adjusting piston 34 moves axially in the direction of the positive x-axis, that is to say in the indicated arrow direction 100. As a result, the adjusting sleeve, together with the imbalance weight 12, rotates in the direction of the arrow 101 and 102, that is, counterclockwise about the x-axis, considering this rotation from the plunger 35 in the direction of the positive x-axis.

Das Tellerrad 43, welches mit dem Unwuchtgewicht 12 fest verbunden ist, dreht sich ebenso wie das Unwuchtgewicht 12 in Pfeilrichtung 102. Dadurch werden die Ritzel 41, 42, welche drehbar auf einem Übertragungsmittelträger 45 angeordnet sind und mit dem Tellerrad 43 über die Kegelverzahnung im Eingriff sind, wobei der Übertragungsmittelträger 45 in einer Querbohrung 49 drehfest mit der Grundwelle 10 verbunden ist, gedreht. Die Drehung der Ritzel 41, 42 erfolgt in angezeigte Pfeilrichtungen 103, 104, also im Uhrzeigersinn, wenn man die Drehung vom Axiallager 48 des Ritzels 42 in Richtung positiver z-Achse beobachtet. Die Drehung der Ritzel 41, 42 verursacht die Verdrehung des Tellerrads 44 und damit auch des Unwuchtgewichtes 13. Allerdings ist aufgrund der Ausführung der Kopplung 40 mittels Kegelräder, d. h. mittels Tellerräder 43, 44 und Ritzel 41, 42, die Drehrichtung des Unwuchtgewichtes 13 (Pfeilrichtung 105) der Drehrichtung des Unwuchtgewichtes 12 entgegengesetzt.The ring gear 43, which is fixedly connected to the imbalance weight 12, rotates in the same direction as the imbalance weight 12 in the direction of arrow 102. As a result, the pinion 41, 42 which are rotatably mounted on a transmission medium carrier 45 and with the ring gear 43 via the conical toothing in engagement are, wherein the transmission medium carrier 45 in a transverse bore 49 rotatably connected to the fundamental shaft 10 is rotated. The rotation of the pinions 41, 42 takes place in indicated arrow directions 103, 104, ie in the clockwise direction, when the rotation is observed from the axial bearing 48 of the pinion 42 in the direction of the positive z-axis. The rotation of the pinion 41, 42 causes the rotation of the ring gear 44 and thus also the imbalance weight 13. However, due to the design of the coupling 40 by means of bevel gears, d. H. by means of ring gears 43, 44 and pinion 41, 42, the direction of rotation of the imbalance weight 13 (arrow 105) opposite to the direction of rotation of the imbalance weight 12.

Es zeigt sich also, dass mit Hilfe der Kopplung 40 eine sehr kompakte und einfache Verstellung der Winkelstellungen der Unwuchtgewichte 12, 13 erreicht wird. Eine Verdrehung des Unwuchtgewichts 12 beispielsweise um 90° gegenüber seiner Ausgangsstellung bezüglich der Unwuchtwelle 10 bewirkt eine Verdrehung des Unwuchtgewichts 13 ebenfalls um 90°, allerdings in die entgegengesetzte Drehrichtung, so dass sich die Unwuchtgewichte 12, 13 relativ zu- oder voneinander um 180° verdrehen. Die Wendelnuten 32 der Verstellhülse 31 sind so ausgelegt, dass sich die Verstellhülse 31 von einer in Fig. 1 gezeigten Stellung (Einstellung für minimale bzw. keine Erregerkraft) zu einer in Fig. 3 gezeigten Stellung (Einstellung für maximale Erregerkraft) um genau 90° drehbar ist. Dadurch können die Unwuchtgewichte jeweils um 90° gegensinnig relativ auf insgesamt 180° verdrehen. Zwischen den Einstellungen für minimale und maximale Erregerkraft ist eine beliebige stufenlose Einstellung möglich.It thus turns out that with the aid of the coupling 40, a very compact and simple adjustment of the angular positions of the imbalance weights 12, 13 is achieved. A rotation of the imbalance weight 12, for example, by 90 ° relative to its starting position with respect to the imbalance shaft 10 causes a rotation of the imbalance weight 13 also by 90 °, but in the opposite direction of rotation, so that the imbalance weights 12, 13 rotate relative to or from each other by 180 ° , The helical grooves 32 of the adjusting sleeve 31 are designed so that the adjusting sleeve 31 of a in Fig. 1 shown position (setting for minimum or no exciter force) to a in Fig. 3 shown position (setting for maximum excitation force) to exactly 90 ° is rotatable. As a result, the imbalance weights can each rotate by 90 ° in opposite directions relative to a total of 180 °. Between the settings for minimum and maximum excitation force, any continuous adjustment is possible.

Die Verdrehung der Unwuchtgewichte 12, 13 erfolgt meist in Betrieb während der Rotation der Grundwelle 10. Bei einem fest eingestellten Phasenunterschied der Unwuchtgewichte 12, 13 werden die drehbar mittels Wälzlager 14, 15 gelagerten Unwuchtgewichte 12 und 13 über die Übertragungsmittel 46, in diesem Fall über die Verzahnung mit den Ritzeln 41, 42 mitgenommen. Dabei stehen die Ritzel still. Die Verbindung über die Verzahnung ist somit als eine statische Verbindung zu betrachten. Die eingestellten Unwuchtgewichte 12, 13 rotieren gleichsinnig mit der Grundwelle. Hierbei wird ein großer Vorteil der erfindungsgemäßen Vorrichtung deutlich. Aufgrund der Ausführung der Kopplung 40 mittels Tellerräder 43, 44 und Ritzel 41, 42 stützen sich die bei der Rotation der Grundwelle 10 auftretenden Massenträgheiten der Unwuchtgewichte 12, 13 gegenseitig über die Ritzel 41, 42 ab, so dass keine ungewollte Verdrehung der Unwuchtgewichte 12, 13 auftreten kann. Die Kopplung 40 samt der Übertragungsmittel 46 begünstigt eine Art Selbstarretierung. Es folgt ferner, dass die Übertragungsmittelträger 45 aufgrund des symmetrischen Eingriffs der Verzahnungsteile in Bezug auf die Symmetrieachse des Übertragungsmittelträgers 45 nur minimale Stützkräfte und Stützmomente aufnehmen müssen, so dass große Vorteile hinsichtlich Lebensdauer und Robustheit der erfindungsgemäßen Kopplung 40 erzielt werden. Zudem kann die Verzahnung beispielsweise als geschmiedete oder gegossene Verzahnungsteile einfach und kostensgünstig ausgeführt sein.The rotation of the imbalance weights 12, 13 is usually in operation during rotation of the fundamental wave 10. At a fixed phase difference of the imbalance weights 12, 13 are rotatably mounted by means of bearings 14, 15 imbalance weights 12 and 13 via the transmission means 46, in this case over the teeth with the pinions 41, 42 taken. The sprockets stand still. The connection via the toothing is thus to be regarded as a static connection. The set imbalance weights 12, 13 rotate in the same direction with the fundamental. Here, a great advantage of the device according to the invention becomes clear. Due to the design of the coupling 40 by means of ring gears 43, 44 and pinion 41, 42, the inertia of the imbalance weights 12, 13 occurring during the rotation of the basic shaft 10 are mutually supported via the pinions 41, 42, so that no unwanted rotation of the imbalance weights 12, 13 may occur. The coupling 40 together with the transmission means 46 favors a kind of self-locking. It also follows that due to the symmetrical engagement of the gearing parts with respect to the axis of symmetry of the transmission medium carrier 45, the transmission medium carriers 45 only have to absorb minimal supporting forces and supporting moments, so that great advantages in terms of service life and robustness of the coupling 40 according to the invention are achieved. In addition, the teeth can be designed, for example, as forged or cast teeth parts easily and inexpensively.

Die Verstellung der Schwingungsamplitude der Erregerkraft in Betrieb mittels gegensinniger Verdrehung der Unwuchtgewichte 12, 13 ist als eine Superposition der Teilbewegungen "Rotation der Unwuchtgewichte 12, 13 mit der Drehzahl der Unwuchtwelle 10" und "gegensinnige Verdrehung der Unwuchtgewichte 12, 13 um einen gewünschten Winkelbetrag" zu betrachten.The adjustment of the oscillation amplitude of the excitation force in operation by means of opposing rotation of the imbalance weights 12, 13 is a superposition of the partial movements "rotation of the imbalance weights 12, 13 with the rotational speed of the imbalance shaft 10" and "opposing rotation of the imbalance weights 12, 13 by a desired angular amount" consider.

Figur 3 zeigt die erfindungsgemäße Vorrichtung 1 in einer Stellung, bei der die Erregerkraft maximal ist, da die Unwuchtgewichte 12, 13 bezüglich der Grundwelle 10 gleiche Winkelstellungen aufweisen. FIG. 3 shows the device 1 according to the invention in a position in which the excitation force is a maximum, since the imbalance weights 12, 13 with respect to the fundamental shaft 10 have the same angular positions.

Figur 4 zeigt einen Längsschnitt der erfindungsgemäßen Vorrichtung 1. Bei diesem Ausführungsbeispiel sind zwei Unwuchtgewichtpaare 11, 21 mit den Unwuchtgewichten 12, 13 und 22, 23 auf der Grundwelle 10 über die Wälzlager 14, 15, 24, 25 drehbar angeordnet. Jedes Unwuchtgewichtpaar 11, 21 weist eine Kopplung 40 bzw. 50 auf. Zusätzlich werden die benachbarten Unwuchtgewichte 13, 22 der Unwuchtgewichtpaare 11, 21 mittels eines formschlüssigen Verbindungselements 19 phasengleich verbunden. Hierdurch wird eine Serienschaltung der Unwuchtgewichtspaare 11, 21 ermöglicht, so dass nur eine einzige Verstelleinrichtung 30 mit nur einem einzigen Unwuchtgewicht 12 verbunden sein muss, um eine gleichzeitige Verstellung aller auf der Unwuchtwelle 10 befindlichen Unwuchtgewichte 12, 13, 22, 23 zu ermöglichen. Alle Unwuchtgewichte 12, 13, 22 23 sind zweckmäßigerweise gleich groß und gleich schwer. Ebenso sind auch die Kopplungen 40 und 50 gleich. FIG. 4 shows a longitudinal section of the device according to the invention 1. In this embodiment, two imbalance weight pairs 11, 21 with the imbalance weights 12, 13 and 22, 23 on the basic shaft 10 via the rolling bearings 14, 15, 24, 25 rotatably arranged. Each imbalance weight pair 11, 21 has a coupling 40 and 50, respectively. In addition, the neighboring ones Unbalance weights 13, 22 of the imbalance weight pairs 11, 21 connected in phase by means of a positive connection element 19. This allows a series connection of the imbalance weight pairs 11, 21, so that only a single adjustment 30 must be connected to only a single imbalance weight 12 to allow simultaneous adjustment of all imbalance weights 12, 13, 22, 23 located on the imbalance shaft 10. All unbalance weights 12, 13, 22 23 are suitably the same size and the same weight. Likewise, the couplings 40 and 50 are the same.

Um von den in Fig. 4 gezeigten Winkelstellungen der Unwuchtgewichte 12, 13, 22, 23 (minimale bzw. keine Erregerkraft) zu den in Fig. 5 gezeigten Winkelstellungen der Unwuchtgewichte 12, 13, 22, 23 (maximale Erregerkraft) zu gelangen, wird die Verstellhülse 31 der Verstelleinheit 30, wie bereits in Zusammenhang mit Fig. 1 bis 3 beschrieben, um 90° verdreht. Die Kopplung 40 bewirkt eine gegensinnige Verdrehung der Unwuchtgewichte 12, 13 um jeweils 90°, so dass die relative Verdrehung der Unwuchtgewichte 12, 13 insgesamt 180° beträgt. Zusammen mit dem Unwuchtgewicht 13 verdreht sich das mit ihm phasengleich und formschlüssig verbundene Unwuchtgewicht 22 des zweiten Unwuchtgewichtpaares 21 um den gleichen Winkelbetrag. Die Kopplung 50 führt zu einer gegensinnigen Verdrehung des Unwuchtgewichtes 23 im Vergleich zu den Unwuchtgewichten 22, 13. Insgesamt läst sich also festhalten, dass durch die Serienschaltung der Unwuchtgewichtpaare 11, 21 die inneren Unwuchtgewichte 13, 22 phasengleich gehalten werden und bei Verstellung in die entgegengesetzte Richtung drehen als die äußeren Unwuchtgewichte 12, 23, die ihrerseits mittels der Kopplungen 40, 50 und des Verbindungselements 19 phasengleich gehalten werden.To get away from the in Fig. 4 shown angular positions of the imbalance weights 12, 13, 22, 23 (minimum or no exciter force) to the in Fig. 5 shown angular positions of the imbalance weights 12, 13, 22, 23 (maximum excitation force) to arrive, the adjusting sleeve 31 of the adjustment unit 30, as already in connection with Fig. 1 to 3 described, rotated by 90 °. The coupling 40 causes an opposite rotation of the imbalance weights 12, 13 by 90 °, so that the relative rotation of the imbalance weights 12, 13 is 180 ° in total. Together with the imbalance weight 13, the imbalance weight 22 of the second imbalance weight pair 21, which is in phase with and positively connected thereto, is rotated by the same angular amount. The coupling 50 leads to an opposing rotation of the imbalance weight 23 in comparison to the imbalance weights 22, 13. Overall, therefore, let it be noted that the internal imbalance weights 13, 22 are kept in phase by the series connection of imbalance weight pairs 11, 21 and in the opposite direction Direction rotate as the outer imbalance weights 12, 23, which in turn are held in phase by means of the couplings 40, 50 and the connecting element 19.

Ein großer Vorteil bei der Anordnung einer geraden Anzahl von in Serie geschalteten Unwuchtgewichtspaaren 11, 21 auf einer Grundwelle 10 liegt darin, dass die Wälzlager 28, 29 der Unwuchtwelle 10 dank der annähernd symmetrischen Auslegung der Unwuchtwelle 10 in Bezug auf die Mitte der Unwuchtwelle 10 nicht durch unerwünschte "Kippmomente" belastet werden.A great advantage in the arrangement of an even number of imbalance weight pairs 11, 21 connected in series on a basic shaft 10 is that the rolling bearings 28, 29 of the imbalance shaft 10, thanks to the approximately symmetrical design of the unbalanced shaft 10 with respect to the center of the imbalance shaft 10 not be burdened by undesirable "tilting moments".

Figur 6 zeigt eine perspektivische Gesamtansicht einer Ausführungsform der Erfindung. Ein hydraulischer Antrieb 90 mit der Antriebswelle 91 treibt eine der beiden Grundwellen 10 oder 60 über Stirnräder (hier nicht dargestellt) direkt an. Über das Stirnradpaar 82, 83 findet die Synchronisierung und Drehsinnumkehr statt, so dass die Unwuchtwellen 10, 60 in Betrieb mit gleicher Drehzahl, jedoch gegensinnig rotieren. Die Grundwellen 10, 60 weisen die gleichen Bestandteile auf. Auch die Funktionsweisen beider Grundwellen 10, 60 stimmen überein. Das Stirnrad 80 ist über Verbindungselemente, wie z. B. Schrauben/ Mutter, fest mit dem ersten Unwuchtgewicht 12 der Grundwelle 10 verbunden und somit auch mit der Verstellhülse 31 der Verstelleinheit 30. Ebenso ist das Stirnrad 81 mit dem Unwuchtgewicht 62 der Grundwelle 60 und mit der Verstellhülse der Verstelleinheit 70 verbunden. Über das Stirnräderpaar lässt sich auch die Verstellbewegung der Unwuchtgewichte 12, 13, 22, 23 der Grundwelle 10 mit der Verstellbewegung der Unwuchtgewichte 62, 63, 65, 66 der Grundwelle 60 synchronisieren und im Drehsinn umkehren. Dadurch lassen sich die hydraulischen Ansteuerungen 37 beider Verstelleinheiten 30, 70 so kombinieren, dass jeweils statt der doppelt wirkenden nur einfach wirkende Hydraulikzylinder verwendet werden können. Wird beispielsweise der Verstellstift 33 der Verstelleinheit 30 in die positive x-Richtung (Fig. 4) "hineingedrückt", so wird über die gegensinnige Synchronisierung mittels der Stirnräder 80, 81 der Verstellstift (hier nicht dargestellt) der Verstelleinheit 70 entsprechend in die negative x-Richtung "herausgedrückt". FIG. 6 shows an overall perspective view of an embodiment of the invention. A hydraulic drive 90 with the drive shaft 91 drives one of the two basic shafts 10 or 60 via spur gears (not shown here) directly. About the Stirnradpaar 82, 83 takes place the synchronization and rotation reversal, so that the imbalance shafts 10, 60 rotate in operation at the same speed, but in opposite directions. The fundamental waves 10, 60 have the same constituents. The modes of operation of both fundamental waves 10, 60 are also identical. The spur gear 80 is connected via connecting elements, such. As screws / nut, fixed to the first imbalance weight 12th connected to the basic shaft 10 and thus also with the adjusting sleeve 31 of the adjusting unit 30. Similarly, the spur gear 81 is connected to the imbalance weight 62 of the basic shaft 60 and the adjusting sleeve of the adjusting unit 70. The adjustment of the imbalance weights 12, 13, 22, 23 of the basic shaft 10 with the adjustment movement of the imbalance weights 62, 63, 65, 66 of the basic shaft 60 can be synchronized via the pair of spur gears and reversed in rotation. As a result, the hydraulic actuators 37 of both adjusting units 30, 70 can be combined in such a way that only single-acting hydraulic cylinders can be used instead of the double-acting ones. If, for example, the adjusting pin 33 of the adjusting unit 30 in the positive x-direction ( Fig. 4 ) is "pressed in", it is on the opposite synchronization by means of the spur gears 80, 81 of the adjusting pin (not shown here) of the adjusting unit 70 "pushed out" accordingly in the negative x-direction.

Mit Hilfe der erfindungsgemäßen Vorrichtung kann die Schwingungsamplitude der Erregerkraft einfach und schnell durch die Verdrehung der Unwuchtgewichte von einem Minimalwert, also 0 kN auf einen Maximalwert, beispielsweise 174 kN, stufenlos und während des Rotierens der Welle verstellt werden. Dabei hat es sich als besonders vorteilhaft erwiesen, dass die Unwuchtgewichte 12, 13, 22, 23 sowie 62, 63, 65, 66 in Betrieb bis zum Erreichen der Nenndrehzahl der Grundwellen 10, 60 in den in Fig. 1, 4 oder 6 gezeigten Winkelstellungen bleiben. Bei diesen Winkelstellungen wird keine gerichtete Schwingung erzeugt. Nach dem Erreichen der Nenndrehzahl können die Unwuchtgewichte so verdreht werden, bis ein gewünschter Betrag der Schwingungsamplitude der Erregerkraft erreicht ist. Hierdurch lässt sich ein "sanftes" Anfahren ermöglichen. Da der Antriebsmotor der erfindungsgemäßen Vorrichtung 1, beispielsweise ein Dieselmotor, konstant bei Nenndrehzahl betrieben werden kann und nur die Verstellung der Erregerkraft einen Einfluss auf den Motorbetrieb ausübt, kann der Antriebsmotor effizient und verbrauchsoptimiert betrieben werden. Das Anfahrverhalten wird insgesamt besser.With the aid of the device according to the invention, the oscillation amplitude of the excitation force can be adjusted easily and quickly by the rotation of the imbalance weights from a minimum value, ie 0 kN to a maximum value, for example 174 kN, continuously and during the rotation of the shaft. It has proven to be particularly advantageous that the imbalance weights 12, 13, 22, 23 and 62, 63, 65, 66 in operation until reaching the rated speed of the fundamental waves 10, 60 in the in Fig. 1 . 4 or 6 remain shown angular positions. At these angular positions no directional vibration is generated. After reaching the rated speed, the imbalance weights can be rotated until a desired amount of vibration amplitude of the exciter force is reached. This allows a "soft" start. Since the drive motor of the device 1 according to the invention, for example a diesel engine, can be operated constantly at rated speed and only the adjustment of the excitation force exerts an influence on engine operation, the drive motor can be operated efficiently and with optimized fuel consumption. The starting behavior is better overall.

Genauso werden beim Ausstellen oder Reversieren der Maschine mit erfindungsgemäßer Vorrichtung 1 die Unwuchtgewichte zunächst bei Nenndrehzahl in die "Nullstellung" verdreht, so dass keine Erregerkräfte erzeugt werden und anschließend die Maschine abgestellt bzw. reversiert. Durch den ständigen Betrieb der erfindungsgemäßen Vorrichtung bei Nenndrehzahl werden unerwünschte Resonanzbereiche vermieden. Dadurch tritt kein "Taumeln" des Walzkörpers auf. Wird die erfindungsgemäße Vorrichtung für bodenverdichtende Maschinen verwendet, so lassen sich beispielsweise unerwünschte Querrillen vermeiden, so dass sich insgesamt die Qualität der Verdichtung verbessern lässt. Die Möglichkeit der schnellen und bequemen Anpassung der Erregerkraft an die lokalen Gegebenheiten trägt ebenso zur Verbesserung bei. Aufgrund der Kompaktheit lässt sich die erfindungsgemäße Vorrichtung 1 auch in bereits bestehende Serienmaschinen problemlos einbauen. Durch die Anpassung der Verdichtungsleistung an den Untergrund wird eine Lärmreduzierung sowohl für die Umgebung als auch für den Fahrer erreicht. Ferner wird die Schwingungsbelastung der Maschinenstruktur erheblich verringert.Similarly, when issuing or reversing the machine with inventive device 1, the imbalance weights are first rotated at rated speed in the "zero position" so that no excitation forces are generated and then turned off the machine or reversed. Due to the constant operation of the device according to the invention at rated speed undesirable resonance ranges are avoided. As a result, no "tumbling" of the rolling body occurs. If the device according to the invention is used for ground-compacting machines, unwanted transverse grooves, for example, can be avoided so that overall the quality of compaction can be improved. The possibility of quick and convenient adaptation of the excitation force to the local conditions also contributes to the improvement. Due to the compactness can the device 1 according to the invention also incorporate easily into existing series machines. By adjusting the compaction performance to the ground noise reduction for both the environment and for the driver is achieved. Furthermore, the vibration load of the machine structure is significantly reduced.

Figuren 7 bis 9 zeigen eine weitere bevorzugte Ausführungsvariante der Erfindung. Im Unterschied zu den in Figuren 4 bis 6 gezeigten Beispielen sind die beiden benachbarten Unwuchtgewichte 13, 22 der Unwuchtgewichtpaare 11 und 21 nicht phasengleich und fest miteinander verbunden, sondern mittels einer zusätzlichen Kopplung 150, welche im Wesentlichen den Kopplungen 40, 50 entspricht, gegeneinander verdrehbar angeordnet. Ferner weist die zweite Grundwelle 60 ein Unwuchtgewicht 160 auf, welches drehfest auf der zweiten Grundwelle 60 angeordnet ist. Durch die Verbindung aller benachbarten Unwuchtgewichte 12, 13, 22, 23 mittels Kopplungen 40, 150, 50 wird die Maschine, welche mit der erfindungsgemäßen Vorrichtung (1) ausgestattet ist, fahr- und lenkbar gemacht. Solche Maschinen können beispielsweise Vibrationsplatten zur Bodenverdichtung sein. FIGS. 7 to 9 show a further preferred embodiment of the invention. Unlike the in FIGS. 4 to 6 As shown, the two adjacent imbalance weights 13, 22 of the imbalance weight pairs 11 and 21 are not connected in phase and fixed to each other, but by means of an additional coupling 150, which essentially corresponds to the couplings 40, 50, arranged rotatable against each other. Furthermore, the second fundamental wave 60 has an imbalance weight 160, which is arranged rotationally fixed on the second fundamental wave 60. By connecting all adjacent imbalance weights 12, 13, 22, 23 by means of couplings 40, 150, 50, the machine, which is equipped with the device (1) according to the invention, made navigable and steerable. Such machines may be, for example, vibration plates for soil compaction.

Figur 7 zeigt eine Einstellung der Unwuchtgewichte 12, 13, 22, 23 für die "Geradeausfahrt" in die angezeigte Pfeilrichtung 170. Hierbei nehmen die Unwuchtgewichte 12, 23 in der y-z-Ebene einen Winkel von + 45° bezüglich der positiven z-Achse ein. Die Unwuchtgewichte 13, 22 weisen einen Winkel von - 45° bezüglich der z-Achse auf. Bei einer synchron gegensinnigen Rotation der Grundwellen 10, 60 in den gezeigten Winkelstellungen wird neben der Vertikalkomponente der Erregerkraft eine Horizontalkomponente erzeugt, wodurch sich die Vorrichtung in die gezeigte Laufrichtung, nämlich in die positive y-Achse, geradeaus bewegt. Der Betrag der Horizontalkomponente ist in einem Bereich verstellbar, so dass die Fahrtgeschwindigkeit optimal angepasst werden kann. Wird die Vorrichtung für eine Vibrationsplatte verwendet, so ist kein separater Antrieb für die Vor- oder Rückwärtsbewegung der Vibrationsplatte notwendig. FIG. 7 shows an adjustment of the imbalance weights 12, 13, 22, 23 for the "straight ahead" in the indicated arrow direction 170. Here, the imbalance weights 12, 23 in the yz plane occupy an angle of + 45 ° with respect to the positive z-axis. The imbalance weights 13, 22 have an angle of -45 ° with respect to the z-axis. In a synchronously opposite rotation of the fundamental waves 10, 60 in the angular positions shown, a horizontal component is generated in addition to the vertical component of the excitation force, whereby the device in the running direction shown, namely in the positive y-axis, moves straight ahead. The amount of the horizontal component is adjustable in a range, so that the travel speed can be optimally adjusted. If the device is used for a vibrating plate, then no separate drive for the forward or backward movement of the vibrating plate is necessary.

Figur 8 zeigt eine Einstellung der Unwuchtgewichte 12, 13, 22, 23 für die "Kurvenfahrt nach links" in die angezeigte Pfeilrichtung 180. Hierfür wird das erste Unwuchtgewicht 12 über die bekannte Verstelleinrichtung 30, die mit dem Unwuchtgewicht 12 fest verbunden ist, ausgehend von der in Fig. 7 gezeigten Winkelstellung um - 45° bezüglich der positiven z-Achse gedreht, so dass die Unwuchtkraft des Unwuchtgewichtes 12 parallel zur z-Achse in Richtung der positiven z-Achse zeigt. Die Kopplung 40 bewirkt eine gegensinnige Verdrehung des Unwuchtgewichtes 13 in Bezug auf das Unwuchtgewicht 12, so dass die Unwuchtgewichte 12, 13 phasengleich sind. Die Kopplungen 150, 50 führen jeweils zur gegensinnigen Verdrehung der benachbarten Unwuchtgewichte 13, 22 bzw. 22, 23, so dass die Unwuchtgewichte die in Fig. 8 gezeigten Winkelstellungen einnehmen. Die Kraftvektoren des "linken" Unwuchtgewichtpaares 21 mit den Unwuchtgewichten 22, 23 weisen in die entgegengesetzte Richtung, so dass sie sich aufheben. Die Kraftvektoren des "rechten" Unwuchtgewichtpaares 11 mit den Unwuchtgewichten 12, 13 dagegen weisen in die gleiche Richtung, so dass sie aufsummiert werden. Im Betrieb wird eine resultierende Erregerkraft gebildet, wodurch neben der gerichteten Schwingung in Richtung der vertikalen z-Achse auch eine horizontale Komponente erzeugt wird, welche eine Kurvenfahrt nach links, also in Richtung der positiven x-Achse ermöglicht. FIG. 8 shows an adjustment of the imbalance weights 12, 13, 22, 23 for the "turning to the left" in the indicated direction of arrow 180. For this purpose, the first imbalance weight 12 via the known adjusting device 30 which is fixedly connected to the imbalance weight 12, starting from the in Fig. 7 shown angular position rotated by - 45 ° with respect to the positive z-axis, so that the unbalance force of the imbalance weight 12 parallel to the z-axis in the direction of the positive z-axis. The coupling 40 causes an opposite rotation of the imbalance weight 13 with respect to the imbalance weight 12, so that the imbalance weights 12, 13 are in phase. The couplings 150, 50 each lead to the opposite rotation of the adjacent Imbalance weights 13, 22 and 22, 23, so that the imbalance weights in Fig. 8 occupy shown angular positions. The force vectors of the "left" imbalance weight pair 21 with the imbalance weights 22, 23 point in the opposite direction so that they cancel each other out. The force vectors of the "right" imbalance weight pair 11 with the imbalance weights 12, 13, however, point in the same direction, so that they are summed up. In operation, a resulting excitation force is formed, which in addition to the directional vibration in the direction of the vertical z-axis, a horizontal component is generated, which allows cornering to the left, ie in the direction of the positive x-axis.

Figur 9 zeigt eine Einstellung der Unwuchtgewichte 12, 13, 22, 23 für die "Kurvenfahrt nach rechts" in die angezeigte Pfeilrichtung 190. Hierfür wird das erste Unwuchtgewicht 12 über die bekannte Verstelleinrichtung 30, die mit dem Unwuchtgewicht 12 fest verbunden ist, ausgehend von der in Fig. 7 gezeigten Winkelstellung um + 45° bezüglich der positiven z-Achse gedreht, so dass die Unwuchtkraft des Unwuchtgewichtes 12 parallel zur y-Achse in Richtung der positiven y-Achse zeigt. Dies führt aufgrund der Kopplung 40 zu einer gegensinnigen Verdrehung des Unwuchtgewichtgewichtes 13 um - 45°. Das Unwuchtgewicht 22 wird aufgrund der Kopplung 150 um + 45° gedreht, also in die gleiche Drehrichtung wie das Unwuchtgewicht 12. Die Kopplung 50 führt zu einer Verdrehung des Unwuchtgewichtes 23 um - 45°. Im Vergleich zu der in Fig. 8 gezeigten Einstellung sind die Kraftvektoren des "linken" Unwuchtgewichtpaares 21 mit den Unwuchtgewichten 22, 23 gleichgerichtet und die Kraftvektoren des "rechten" Unwuchtgewichtpaares 11 mit den Unwuchtgewichten 12, 13 entgegen gerichtet. Hierdurch wird im Betrieb die Kurvenfahrt nach rechts, also in Richtung der negativen x-Achse, ermöglicht. FIG. 9 shows an adjustment of the imbalance weights 12, 13, 22, 23 for the "cornering to the right" in the indicated arrow direction 190. For this purpose, the first imbalance weight 12 via the known adjusting device 30 which is fixedly connected to the imbalance weight 12, starting from the in Fig. 7 shown angular position rotated by + 45 ° with respect to the positive z-axis, so that the unbalance force of the imbalance weight 12 shows parallel to the y-axis in the direction of the positive y-axis. This leads due to the coupling 40 to an opposite rotation of the imbalance weight 13 by - 45 °. The imbalance weight 22 is rotated by + 45 ° due to the coupling 150, ie in the same direction of rotation as the imbalance weight 12. The coupling 50 leads to a rotation of the imbalance weight 23 by - 45 °. Compared to the in Fig. 8 shown setting the force vectors of the "left" imbalance weight pair 21 with the imbalance weights 22, 23 are rectified and the force vectors of the "right" imbalance weight pair 11 with the imbalance weights 12, 13 directed against. As a result, the cornering to the right during operation, ie in the direction of the negative x-axis, allows.

Mit Hilfe des in Figuren 7 bis 9 gezeigten, erfindungsgemäßen Beispiels kann auf einfache und kompakte Weise eine fahr- und lenkbare Maschine, insbesondere Vibrationsplatte zur Bodenverdichtung, realisiert werden, wobei die Fahrgeschwindigkeit und die Amplitude der Erregerkraft je nach Bedarf optimal angepasst werden können.With the help of in FIGS. 7 to 9 shown example according to the invention can be realized in a simple and compact manner a traveling and steerable machine, in particular vibration plate for soil compaction, the driving speed and the amplitude of the excitation force can be optimally adjusted as needed.

Figur 10 zeigt eine besonders kompakte und einfache Ausführungsvariante der erfindungsgemäßen Vorrichtung. Die erste Grundwelle 10 umfasst nur ein Unwuchtgewichtpaar 11 mit den drehbar gelagerten Unwuchtgewichten 12, 13 und eine zwischen den Unwuchtgewichten 12, 13 angeordnete Kopplung 40 sowie eine Verstelleinrichtung 30, welche mit dem ersten Unwuchtgewicht 12 verbunden ist. Mit der ersten Grundwelle 10 ist eine zweite Grundwelle 60 formschlüssig gekoppelt, wobei die zweite Unwuchtwelle ein drehfest auf ihr angeordnetes Unwuchtgewicht 160 aufweist. Die Verstellung der Winkelstellungen der Unwuchtgewichte 12, 13 erfolgt auf bisher beschriebene, erfindungsgemäße Weise. Durch diese Anordnung der Unwuchtgewichte kann im Betrieb, also bei der synchron gegensinnigen Rotation der Grundwellen 10, 60, ein kontrollierbares "Taumeln" infolge des auftretenden Kippmoments eingestellt werden, wenn die Unwuchtgewichte nicht phasengleich sind. Dadurch kann die Maschine, beispielsweise eine Vibrationsplatte, eine Kurvenfahrt nach rechts oder links ausführen. Nach erfolgter Kurvenfahrt kann während des Betriebes dann wieder auf einfache und bequeme Weise in den Normalbetrieb gewechselt werden. FIG. 10 shows a particularly compact and simple embodiment of the device according to the invention. The first basic shaft 10 comprises only one imbalance weight pair 11 with the rotatably mounted imbalance weights 12, 13 and a coupling 40 arranged between the imbalance weights 12, 13 and an adjusting device 30 which is connected to the first imbalance weight 12. With the first fundamental wave 10, a second fundamental wave 60 is positively coupled, wherein the second imbalance shaft has a non-rotatably mounted on it imbalance weight 160. The adjustment of the angular positions of the imbalance weights 12, 13 takes place in the manner described above according to the invention. As a result of this arrangement of the imbalance weights, a controllable "wobble" due to the occurring tilting moment can be set during operation, that is to say in the synchronously opposite rotation of the basic shafts 10, 60, if the imbalance weights are not in phase. This allows the machine, such as a vibrating plate, to turn right or left. After cornering can then be changed during operation again in a simple and convenient way to normal operation.

Claims (15)

  1. An apparatus of a,soil compaction machine, especially a circular exciter, for generating a variable rotating exciter force by means of a rotating primary shaft (10), with the primary shaft (10) comprising unbalanced weights (12, 13) and a coupling (40) between the unbalanced weights (12, 13), and with the vibration amplitude of the exciter force being adjustable to or from one another in operation by means of an adjusting unit (30) between a minimum and a maximum value in an infinitely variable way via the relative rotation of the unbalanced weights (12, 13), with the unbalanced weights (12, 13) being held on the primary shaft (10) to be rotatable about said primary shaft, characterized in that the coupling (40) comprises a transmission means (46) which is connected with the primary shaft (10) in a torsion-proof way, which transmission means is arranged in such a way that it acts as a driver on the unbalanced weights (12, 13) and further causes an adjustment of the vibration amplitude of the exciter force by the twisting of the unbalanced weights (12, 13) in opposite directions, with one of the unbalanced weights (12) being connected with the adjusting unit (30).
  2. An apparatus for generating a directed vibration (1) with two apparatuses according to claim 1, wherein the primary shafts (10, 60) of these apparatuses are arranged in parallel and rotate synchronously in opposite directions.
  3. An apparatus according to claim 1 or 2, wherein the coupling (40) comprises an apparatus with bevel gears, especially with at least one pinion gear (41) and two ring gears (43, 44), and one respective unbalanced weight (12, 13) comprises a ring gear (43, 44) and the transmission means is the at least one pinion gear (41) which is in engagement with the two ring gears (43, 44).
  4. An apparatus according to one of the preceding claims, wherein the coupling (40) comprises several transmission means (46) which are each arranged in an offset manner about an angle, preferably about the same angle.
  5. An apparatus according to one of the preceding claims, wherein the transmission means (46) is rotatably arranged on a transmission means support (45) and comprises a rotational axis which perpendicularly intersects the rotational axis of the primary shaft.
  6. An apparatus according to claim 5, wherein the primary shaft (10) comprises at least one transverse bore (49) for receiving the transmission means support (45).
  7. An apparatus according to claim 5 or 6, wherein means (48), especially thrust bearings, are arranged for absorbing centrifugal forces which are produced by the transmission means (41).
  8. An apparatus according to one of the claims 5 to 7, wherein the transmission means (46) are held in a floating manner on the transmission means support (45).
  9. An apparatus according to one of the preceding claims, wherein the primary shaft (10) comprises a number of pairs of unbalanced weights (11, 21) with unbalanced weights (12, 13, 22, 23) of equal size, with each pair of unbalanced weights (11, 21) comprising an interposed coupling (40, 50).
  10. An apparatus according to claim 9, wherein the pairs of unbalanced weights (11, 21) are connected in series in such a way that adjacent unbalanced weights (13, 22) of the pairs of unbalanced weights (11, 21) are connected with one another in phase in a preferably interlocking manner.
  11. An apparatus according to one of the preceding claims, wherein the unbalanced weights (12, 13, 22, 23) comprise means for reducing axial play (17), especially spring elements.
  12. An apparatus according to claim 9 or 10, wherein the primary shaft (10) comprises an even number of pairs of unbalanced weights (11, 21) which are connected in series.
  13. An apparatus according to one of the preceding claims, wherein the pairs of unbalanced weights (11, 21) are connected with one another by way of a further coupling (150).
  14. An apparatus according to one of the preceding claims, wherein the second primary shaft (60) comprises an unbalanced weight (160) which is connected with it in a torsion-proof manner.
  15. The use of an apparatus for generating a directed vibration (1) according to claim 14 for a vibration plate for soil compaction, wherein the vibration plate is drivable and steerable.
EP09010928A 2008-10-06 2009-08-26 Device for generating a circuit vibration or a directed vibration with infinitely adjustable vibration amplitude or exciter power Active EP2172279B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102008050576A DE102008050576A1 (en) 2008-10-06 2008-10-06 Device for generating a circular oscillation or a directed oscillation with continuously adjustable oscillation amplitude or exciter force

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EP2172279A1 EP2172279A1 (en) 2010-04-07
EP2172279B1 true EP2172279B1 (en) 2011-07-13

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US (1) US20100147090A1 (en)
EP (1) EP2172279B1 (en)
JP (1) JP5380234B2 (en)
CN (1) CN101961710B (en)
AT (1) ATE516089T1 (en)
DE (1) DE102008050576A1 (en)

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EP2172279A1 (en) 2010-04-07
JP2010099656A (en) 2010-05-06
ATE516089T1 (en) 2011-07-15
US20100147090A1 (en) 2010-06-17
CN101961710B (en) 2012-11-14
JP5380234B2 (en) 2014-01-08
CN101961710A (en) 2011-02-02
DE102008050576A1 (en) 2010-04-08

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