EP2172279B1 - Dispositif de production d'une oscillation circulaire ou d'une oscillation orientée dotée d'une amplitude d'oscillation ou d'une force d'excitation réglable en continu - Google Patents

Dispositif de production d'une oscillation circulaire ou d'une oscillation orientée dotée d'une amplitude d'oscillation ou d'une force d'excitation réglable en continu 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
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Prior art keywords
weights
imbalance
unbalanced weights
transmission means
vibration
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EP09010928A
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German (de)
English (en)
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EP2172279A1 (fr
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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Claims (15)

  1. Dispositif d'une machine pour compacter le sol, en particulier vibrateur rotatif, pour produire une force d'excitation rotative variable au moyen d'un arbre de base rotatif (10), dans lequel l'arbre de base (10) présente des masses de balourd (12, 13) ainsi qu'un accouplement (40) entre les masses de balourd (12, 13) et dans lequel l'amplitude de vibration de la force d'excitation peut être réglée en continu en fonctionnement entre une valeur minimale et une valeur maximale au moyen d'une unité de réglage (30) à l'aide de la rotation relative des masses de balourd (12, 13) se rapprochant ou s'éloignant les unes des autres,
    dans lequel les masses de balourd (12, 13) sont supportées sur l'arbre de base (10) avec possibilité de rotation autour de celui-ci,
    caractérisé en ce que l'accouplement (40) comprend un moyen de transmission (46) solidaire en rotation de l'arbre de base (10), qui est conçu de telle manière qu'il agit comme un entraîneur sur les masses de balourd (12, 13) et réalise en outre un réglage de l'amplitude de vibration de la force d'excitation par la rotation des masses de balourd (12, 13) en sens inverse l'une de l'autre, l'une des masses de balourd (12) étant reliée à l'unité de réglage (30).
  2. Dispositif pour produire des vibrations directionnelles (1) avec deux dispositifs selon la revendication 1, dans lequel les arbres de base (10, 60) de ces dispositifs sont disposés parallèlement l'un à l'autre et tournent de manière synchrone en sens inverse l'un de l'autre.
  3. Dispositif selon la revendication 1 ou 2, dans lequel l'accouplement (40) présente un dispositif avec des roues coniques, en particulier avec au moins un pignon (41) et deux couronnes (43, 44), et chaque masse de balourd (12, 13) présente une couronne (43, 44) et le moyen de transmission est l'au moins un pignon (41), qui engrène avec les deux couronnes (43, 44).
  4. Dispositif selon l'une des revendications précédentes, dans lequel l'accouplement (40) présente plusieurs moyens de transmission (46) décalés selon un angle, de préférence selon le même angle.
  5. Dispositif selon l'une des revendications précédentes, dans lequel le moyen de transmission (46) est disposé avec possibilité de rotation sur un support de moyen de transmission (45) et présente un axe de rotation qui coupe perpendiculairement l'axe de rotation de l'arbre de base.
  6. Dispositif selon la revendication 5, dans lequel l'arbre de base (10) présente au moins un alésage transversal (49) pour recevoir le support de moyen de transmission (45).
  7. Dispositif selon la revendication 5 ou 6, dans lequel sont disposés sur le support de moyen de transmission (45) des moyens (48), en particulier des paliers axiaux, pour absorber les forces centrifuges produites par le moyen de transmission (41).
  8. Dispositif selon l'une des revendications 5 à 7, dans lequel les moyens de transmission (46) sont supportés de manière flottante sur le support de moyen de transmission (45).
  9. Dispositif selon l'une des revendications précédentes, dans lequel l'arbre de base (10) présente plusieurs paires de masses de balourd (11, 21) avec des masses de balourd (12, 13, 22, 23) de même taille, chaque paire de masses de balourd (11, 21) comprenant un accouplement (40, 50) disposé entre celles-ci.
  10. Dispositif selon la revendication 9, dans lequel les paires de masses de balourd (11, 21) sont montées en série par le fait que des masses de balourd (13, 22) voisines des paires de masses de balourd (11, 21) sont reliées entre elles avec la même phase, de préférence en correspondance de forme.
  11. Dispositif selon l'une des revendications précédentes, dans lequel les masses de balourd (12, 13, 22, 23) présentent des moyens pour réduire le jeu axial (17), en particulier des éléments formant ressort.
  12. Dispositif selon la revendication 9 ou 10, dans lequel l'arbre de base (10) présente un nombre pair de paires de masses de balourd (11, 21) qui sont montées en série.
  13. Dispositif selon l'une des revendications précédentes, dans lequel les paires de masses de balourd (11, 21) sont reliées entre elles par l'intermédiaire d'un autre accouplement (150).
  14. Dispositif selon l'une des revendications précédentes, dans lequel le deuxième arbre de base (60) présente une masse de balourd (160) qui lui est reliée de manière solidaire en rotation.
  15. Utilisation d'un dispositif pour la production de vibrations directionnelles (1) selon la revendication 14 pour une plaque vibrante servant au compactage du sol, dans laquelle la plaque vibrante peut être conduite et dirigée.
EP09010928A 2008-10-06 2009-08-26 Dispositif de production d'une oscillation circulaire ou d'une oscillation orientée dotée d'une amplitude d'oscillation ou d'une force d'excitation réglable en continu Active EP2172279B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102008050576A DE102008050576A1 (de) 2008-10-06 2008-10-06 Vorrichtung zur Erzeugung einer Kreisschwingung oder einer gerichteten Schwingung mit stufenlos verstellbarer Schwingungsamplitude bzw. Erregerkraft

Publications (2)

Publication Number Publication Date
EP2172279A1 EP2172279A1 (fr) 2010-04-07
EP2172279B1 true EP2172279B1 (fr) 2011-07-13

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EP09010928A Active EP2172279B1 (fr) 2008-10-06 2009-08-26 Dispositif de production d'une oscillation circulaire ou d'une oscillation orientée dotée d'une amplitude d'oscillation ou d'une force d'excitation réglable en continu

Country Status (6)

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

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DE102014008116A1 (de) 2014-06-03 2015-12-03 Bomag Gmbh Verfahren zur schmiermittelversorgung eines getriebes, getriebeschmiereinrichtung, getriebeeinheit und baumaschine

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US8347984B2 (en) * 2009-04-29 2013-01-08 Longyear™, Inc. Variable force/variable frequency sonic drill head
EP2325391B1 (fr) * 2009-11-20 2013-03-20 Joseph Vögele AG Dispositif de bourrage à course variable
DE102010010037B4 (de) * 2010-03-03 2019-10-31 Bomag Gmbh Stufenlos verstellbarer Schwingungserreger
DE102010021961A1 (de) * 2010-05-28 2012-04-19 Bomag Gmbh Schwingungserreger für ein Bodenverdichtungsgerät und Bodenverdichtungsgerät
US8393826B1 (en) 2011-08-31 2013-03-12 Caterpillar Inc. Apparatus for transferring linear loads
DE102011112316B4 (de) * 2011-09-02 2020-06-10 Bomag Gmbh Schwingungserreger zur Erzeugung einer gerichteten Erregerschwingung
EP2789403B1 (fr) * 2013-04-10 2015-12-16 ABI Anlagentechnik-Baumaschinen-Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH Générateur de vibrations pour machines de construction
EP2789402B1 (fr) * 2013-04-10 2017-05-17 ABI Anlagentechnik-Baumaschinen-Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH Accélérateur d'oscillations
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JP5380234B2 (ja) 2014-01-08
EP2172279A1 (fr) 2010-04-07
ATE516089T1 (de) 2011-07-15
CN101961710A (zh) 2011-02-02
CN101961710B (zh) 2012-11-14
JP2010099656A (ja) 2010-05-06
DE102008050576A1 (de) 2010-04-08

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