EP2158976B1 - Dispositif de production de vibrations - Google Patents

Dispositif de production de vibrations Download PDF

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Publication number
EP2158976B1
EP2158976B1 EP08015096.4A EP08015096A EP2158976B1 EP 2158976 B1 EP2158976 B1 EP 2158976B1 EP 08015096 A EP08015096 A EP 08015096A EP 2158976 B1 EP2158976 B1 EP 2158976B1
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EP
European Patent Office
Prior art keywords
shaft
groups
swivel
motor
vibration
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP08015096.4A
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German (de)
English (en)
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EP2158976A1 (fr
Inventor
Christian Heichel
Albrecht Kleibl
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ABI Anlagentechnik Baumaschinen Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH
Original Assignee
ABI Anlagentechnik Baumaschinen Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH
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Priority to EP08015096.4A priority Critical patent/EP2158976B1/fr
Priority to US12/459,692 priority patent/US8225685B2/en
Publication of EP2158976A1 publication Critical patent/EP2158976A1/fr
Application granted granted Critical
Publication of EP2158976B1 publication Critical patent/EP2158976B1/fr
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Classifications

    • 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
    • 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
    • Y10T74/18544—Rotary to gyratory
    • Y10T74/18552—Unbalanced weight

Definitions

  • the invention relates to a vibration generator according to the preamble of patent claim 1.
  • vibrators are used to bring objects such as profiles into the ground or to pull them out of the ground or to compact soil material.
  • the soil is stimulated by vibration and thus reaches a "pseudo-liquid state".
  • By static load the pile can then be pressed into the ground.
  • the vibration is characterized by a linear movement and is generated by pairwise counter-rotating imbalances within a Vibratorgetriebes.
  • the vibration generators are linear vibration exciters whose centrifugal force is generated by rotating imbalances. These vibration exciters move at a variable speed.
  • the size of the unbalance is also called a static moment.
  • the course of the velocity of the linear vibration exciter corresponds to a periodically recurring function, in particular a sine function. Due to the sinusoidal course of the force generated by means of the rotating unbalanced masses a temporally offset alternately acting in and against the direction of advance drive is generated. This is ultimately determined by static forces, in particular dead weight and static loads. Without the superimposition of the vibration with static forces, the pile would not move forward, but would merely swing back and forth.
  • the publication DE 196 39 789 discloses such a vibrator.
  • the piling with the aforementioned sinusoidal force curve has a considerable energy consumption, which is additionally increased by friction of the pile in the ground.
  • the energy used for the vibrator causes virtually no propulsion.
  • the force curve of each imbalance group describes a sinusoid.
  • the summation of the individual force curves results in a course in which the magnitudes of the amplitude in the direction in which the forces are superimposed are greater than the magnitudes of the amplitude in the opposite direction.
  • This approach results in a significant propulsion, whereby the efficiency of the piling operation is increased.
  • the degree of efficiency depends on the respective required speed, the pile mass, the construction process and the respective soil conditions.
  • the document DE 20 2007 005 283 discloses a vibration generator in which the rotational position of the imbalance masses to each other can be changed by means of a phase shift.
  • the invention aims to remedy this situation.
  • the invention is based on the object to provide a vibration generator with a directed force in the forward direction, in which a change in the resulting static moment of at least one wave group is also possible during operation. According to the invention, this object is solved by the features of the characterizing part of patent claim 1.
  • a vibration generator is provided with directed force in the direction of advance, in which a change in the resulting moment of at least one wave group is also possible during operation.
  • the vibration generator according to the invention it is possible to set the static moment of the individual wave groups independently of one another. As a result, the characteristic of the vibrator can be adapted to the individual case.
  • One and the same vibration generator can thus generate different frequencies at the same speed of the drive motors by zeroing the static torque on different wave groups.
  • phase shifter is to be understood below as a device which is suitable for effecting an adjustment of the relative position of two rotating objects (such as, for example, waves or imbalances) to one another.
  • shaft group is understood below an arrangement of waves that are constantly coupled to each other at the same speed to each other.
  • imbalance groups can be arranged on one shaft group.
  • the phase shifter is formed by a swivel motor.
  • the use of a swing motor allows relative adjustment of the unbalance groups of a wave group to each other, without the conversion of a linear movement is required in a rotary motion, whereby a compact design is achieved.
  • the swivel motor is preferably a swivel-blade rotary motor, with a swivel motor shaft and a swivel motor housing, both the swivel motor shaft and the swivel motor housing with imbalances in each case at least one shaft group is connected and the rotational position of the pivot motor housing is variable relative to the pivot motor shaft.
  • the swivel motor has means for locking the swivel motor housing with the swivel motor shaft. Due to the means for locking the swivel motor housing with the swivel motor shaft, a change in position due to internal leakage is avoided. Since in the locked state of the swivel motor housing, the hydraulic pressure can be reduced, the seals are significantly less stressed, resulting in less wear of the seals result, since in the unpressurized state, the contact forces are significantly lower. Furthermore, an energy saving is effected because over the period of operation of the vibrator no adjustment or adjustment of the swing motor is required. Furthermore, the required control of the swing motor is simplified.
  • the means for locking the swivel motor housing with the swing motor shaft is hydraulically actuated.
  • the brake system can be connected to the existing hydraulics.
  • the means for locking the swivel motor housing with the swivel motor shaft is formed by a spring pressure multi-disc brake.
  • Such multi-disc brakes require only a small space.
  • two wave groups are arranged on which at least two imbalance groups are arranged, the wave groups are connected to the at least one drive so that the speed of the shaft group is half the speed of the shaft group and that the ratio of the static moments with the unbalanced groups provided wave groups between six to one and ten to one.
  • the static moment of the first wave group is eight times as large as the static moment of the second wave group.
  • a pronounced force peak is effected in the advancing direction.
  • three wave groups are arranged on which at least three unbalance groups are arranged, the wave groups are connected to the at least one drive so that the speed of the shaft group is half the speed of the shaft group and one third of the speed of the shaft group and the ratio of the static moments of the imbalance groups provided with the imbalance groups is substantially 100: 16.64: 3.68.
  • the maximum-acting force is increased by a further pronounced force peak in the direction of advance, causing a further increase in energy efficiency, combined with an acceleration of the piling process, is effected.
  • four wave groups are arranged on which at least four imbalance groups are arranged, wherein the wave groups are connected to the at least one drive such that the ratio of the rotational speeds of the wave groups to one another is substantially 1: 2: 3: 4 and that the ratio of the static moments of the imbalance groups provided with the imbalance groups) is substantially 100: 18.72: 5.6: 1.38.
  • the force curve is achieved in the direction of advance.
  • means for adjusting the effective direction of the vibrator are provided. This allows adaptation of the vibrator to different process requirements such as ramming and pulling.
  • the means for adjusting the direction of action include a phase shifter, via which the relative position of at least two wave groups to one another during operation is variable.
  • a conversion of the effective direction is made possible without any necessary conversion measures.
  • the phase shifter is formed by a pivot motor.
  • the at least two wave groups are connected via gears with the pivot motor, wherein an imbalance group with the stator and a shaft group is connected to the rotor of the swing motor.
  • the swing motor is a rotary vane with multiple blades. This is distinguished from swing motors with a wing by multiple times higher torque and lower friction.
  • the vibration generator chosen as the embodiment are designed as vibrator gear.
  • Such vibrators essentially consist of a housing in which gears provided with gears are rotatably mounted.
  • the gears are each provided with imbalance masses.
  • Such Vibratorgetriebe with rotatably mounted imbalance masses are the expert, for example from the DE 20 2007 006 283 U1 known.
  • the following explanation of the embodiments is essentially limited to the arrangement of waves and imbalance masses.
  • each with three shafts 11, 12, 13, 21, 22, 23 arranged, each with two gears 112, 113, 122, 123, 132, 133, 212, 213, 222, 223, 232, 233 are provided, on which in turn in each case unbalanced masses 111, 114, 121, 124, 131, 134, 211, 214, 221, 224, 231, 234 are arranged.
  • the number of waves of the wave groups 1, 2 can also be chosen differently.
  • a swing motor 5 is arranged such that the gear 51 of the housing (stator) of the swing motor 5 with the gear 113 is engaged and the gear 52 of the shaft (rotor) of the swing motor 5 with the gear 212 in engagement is.
  • the pivot motor 5 is a rotary wing pivot motor with three wings.
  • the gear 132 of the shaft group 1 is engaged with the gear 62 of the rotor of another swing motor 6 and the gear 133 of the shafts of the shaft group 1 with the gear 61 of the stator of the swing motor 6 in engagement.
  • another pivoting motor 7 with its gears 71, 72 with the gears 232, 233 of the shaft 23 of the shaft group 2 is engaged.
  • This consists in principle of two Verstellvibratoren in which the static torque is independent of each other adjustable and in which the phase angle of the two wave groups can be arbitrarily shifted against each other via the central pivot motor 5.
  • the length of this vibrator is shorter by an offset arrangement of the smaller waves 21, 22, 23 of the shaft group 2 executable.
  • the pivot motor 6 is - as well as the pivot motors 5 and 7 - essentially formed by a pivot motor shaft 60 and a surrounding pivot motor housing 610 to which a gear 61 is integrally formed, and two on both sides of the pivot motor housing arranged closure cap 63. Between the swing motor shaft 60 and the pivot motor housing 610, a gap is formed, which is divided by an integrally formed on the pivot motor shaft 60 rotor blades 601 and by an integrally formed on the pivot motor housing 610 stator vanes 612, so that two working spaces 64a, 64b are formed.
  • the stator blade 612 is formed directly on the inside of the gear 61, so that the swivel motor housing 610 with gear 61 and stator vanes 612 are integrally formed.
  • a shuttle valve 613 is arranged in the stator vanes 612, the control channels of which open on both sides of the stator vanes into the work spaces 64a, 64b (cf. FIG. 5 ).
  • 60 channels 602 for media supply of the working chambers and the multi-disc brake 65 are introduced longitudinally in the shaft through the hydraulic system.
  • a gear 62 is further arranged on the pivot motor shaft.
  • the swivel motor is provided with a multi-disc brake 65.
  • the multi-disc brake 65 consists of a housing 630 fixed to the cover 63 of the swivel motor housing 610, a hub 606 secured to the shaft 60 and a clutch disc package 65. If the clutch discs meshing with the housing 630 become mechanically resilient by spring force (or alternatively hydraulically) against that with the swivel motor shaft 60 connected hub clutching clutch discs pressed, a locking of the pivot motor housing 610 is effected with the swing motor shaft 60.
  • the gear 61 is rotated relative to the pivot motor shaft 60 and thus also rotatably connected to the pivot motor shaft 60 gear 62.
  • the gears 133, 123, 113 engaged with the gear 61 of the swing motor housing 610 are changed in their rotational position, so that the imbalance masses 134, 124, 114 of an imbalance group are displaced with respect to the imbalance masses 131, 121, 111 of the opposing imbalance group, causing a change the resulting imbalance is effected.
  • FIG. 2 is a modified structure of the above arrangement of the wave groups shown (with pivot motors 5, 6, 7), which allows a significant reduction in length, but in place of six waves eight waves are required, but this in a lower load on the shaft bearings precipitates and brings benefits in terms of achievable centrifugal force, the suitability for high speeds and a lower sensitivity to large angular accelerations.
  • an additional speed stage whose unbalance rotate at three times speed can be used.
  • FIG. 3 such an arrangement is shown.
  • the adjustment of the direction of action is carried out by the pivot motor 5, which the wave group 2 with respect to the wave group 1, which is coupled to the wave group 3, adjusted.
  • the pivot motor 5 When adjusting the effective direction, the angular position of the shaft group 1 and shaft group 3 remains unchanged.
  • the pivot motor 5 the adjustment of the shaft group 2 with respect to the other is possible.
  • the swivel motor 6 is used to adjust the resulting imbalance of the shaft group 1 by changing the relative position of the first imbalance group formed by the imbalances 111, 121, 131 against the second imbalance group formed by the imbalances 114, 124, 134. All in all, the swivel motor 7 serves to adjust the resulting imbalance of the shaft group 2 and the swivel motor 8 to adjust the resulting imbalance of the shaft group 3.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)

Claims (12)

  1. Dispositif générateur de vibrations comprenant au moins deux groupes d'arbres sur lesquels sont agencés au moins deux groupes de masselottes et qui sont reliés avec au moins un entraînement les faisant entrer en rotation, sachant qu'au moins deux groupes d'arbres (1, 2) sont reliés avec au moins un entraînement de sorte que la vitesse d'au moins un groupe d'arbres (2) représente un multiple de la vitesse d'au moins un autre groupe d'arbres (1), et qu'au moins deux des groupes d'arbres (1, 2) équipés des groupes de masselottes (101, 102) présentent chacun des moments statiques différents l'un de l'autre, caractérisé en ce qu'au moins un groupe d'arbres (1, 2) est relié à un dispositif de décalage de phase (6, 7) via lequel il est possible de régler le moment statique du groupe d'arbres (1, 2), sachant que sont prévus des moyens destinés à déplacer la direction active du dispositif générateur de vibrations, lesquels moyens comprennent un autre dispositif de décalage de phase (5) via lequel il est possible de modifier en service la position relative mutuelle d'au moins deux groupes d'arbres (1, 2).
  2. Dispositif générateur de vibrations selon la revendication 1, caractérisé en ce que le dispositif de décalage de phase est formé par un moteur pivotant (6, 7).
  3. Dispositif générateur de vibrations selon la revendication 2, caractérisé en ce que le moteur pivotant est un moteur à pales rotatives comprenant un arbre (60) de moteur pivotant et un carter (610) de moteur pivotant, sachant qu'aussi bien l'arbre (60) du moteur pivotant que le carter (610) du moteur pivotant sont reliés aux masselottes d'au moins un groupe d'arbres et qu'il est possible de modifier la position de rotation du carter (610) du moteur pivotant relativement à l'arbre (60) du carter pivotant.
  4. Dispositif générateur de vibrations selon la revendication 2 ou 3, caractérisé en ce que le moteur pivotant (6) présente des moyens (65) permettant de retenir le carter (610) du moteur pivotant avec l'arbre (60) du moteur pivotant.
  5. Dispositif générateur de vibrations selon la revendication 4, caractérisé en ce que le moyen (65) servant à retenir le carter (610) du moteur pivotant est actionnable hydrauliquement avec l'arbre (60) du moteur pivotant.
  6. Dispositif générateur de vibrations selon la revendication 4 ou 5, caractérisé en ce que le moyen servant à retenir le carter (610) du moteur pivotant avec l'arbre (60) du moteur pivotant est formé par un frein à lamelles (65, 616, 630) sous pression d'un ressort.
  7. Dispositif générateur de vibrations selon l'une des revendications 1 à 6, caractérisé en ce que sont agencés deux groupes d'arbres sur lesquels sont agencés au moins deux groupes de masselottes, sachant que les groupes d'arbres (1, 2) sont reliés de telle sorte avec au moins un entraînement que la vitesse du groupe d'arbres (1) représente la moitié de la vitesse du groupe d'arbres (2) que le rapport entre les moments statiques des groupes d'arbres (1, 2) équipés des groupes de masselottes (101, 201) est compris entre 6 : 1 et 10 : 1.
  8. Dispositif générateur de vibrations selon la revendication 7, caractérisé en ce que le moment statique du groupe d'arbres (1) est huit fois plus important que le moment statique du groupe d'arbres (2).
  9. Dispositif générateur de vibrations selon l'une des revendications 1 à 6, caractérisé en ce que sont agencés trois groupes d'arbres sur lesquels sont agencés au moins trois groupes de masselottes, sachant que les groupes d'arbres (1, 2, 3) sont reliés avec au moins un entraînement de sorte que la vitesse du groupe d'arbres (1) représente la moitié de la vitesse du groupe d'arbres (2) et un tiers de la vitesse du groupe d'arbres (3), et que le rapport mutuel entre moments statiques des groupes d'arbres (1, 2, 3) équipés des groupes de masselottes s'élève essentiellement à 100 : 16,64 : 3,68.
  10. Dispositif générateur de vibrations selon l'une des revendications 1 à 6, caractérisé en ce que sont agencés quatre groupes d'arbres sur lesquels sont agencés au moins quatre groupes de masselottes, sachant que les groupes d'arbres (1, 2, 3, 4) sont reliés avec un entraînement de telle sorte que le rapport mutuel entre vitesses des groupes d'arbres (1, 2, 3, 4) s'élève à 1 : 2 : 3 : 4 et que le rapport mutuel des moments statiques que présentent les groupes d'arbres (1, 2, 3, 4) équipés de groupes de masselottes s'élève essentiellement à 100 : 18,72 : 5,6 : 1,38.
  11. Dispositif générateur de vibrations selon la revendication 1, caractérisé en ce que le dispositif de décalage de phase suivant est configuré en moteur pivotant (5).
  12. Dispositif générateur de vibrations selon la revendication 11, caractérisé en ce qu'au moins deux groupes d'arbres (1, 2) sont reliés au moteur pivotant (5) via des engrenages (212, 213), sachant qu'un groupe d'arbres est relié au stator et qu'un groupe de masselottes est relié au rotor du moteur pivotant (5).
EP08015096.4A 2008-08-27 2008-08-27 Dispositif de production de vibrations Active EP2158976B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP08015096.4A EP2158976B1 (fr) 2008-08-27 2008-08-27 Dispositif de production de vibrations
US12/459,692 US8225685B2 (en) 2008-08-27 2009-07-07 Vibration generator

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP08015096.4A EP2158976B1 (fr) 2008-08-27 2008-08-27 Dispositif de production de vibrations

Publications (2)

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EP2158976A1 EP2158976A1 (fr) 2010-03-03
EP2158976B1 true EP2158976B1 (fr) 2013-08-14

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202015003475U1 (de) 2015-02-11 2016-05-12 Liebherr-Components Biberach Gmbh Rüttler
EP3165290A1 (fr) 2015-11-06 2017-05-10 BAUER Maschinen GmbH Dispositif de production de vibrations et procede d'introduction de profile dans un sol
WO2020224918A1 (fr) 2019-05-08 2020-11-12 Liebherr-Components Biberach Gmbh Générateur de vibrations ainsi qu'engin de chantier comportant un tel générateur de vibrations

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010043187A1 (fr) * 2008-10-14 2010-04-22 Francisco Pacheco Appareil d'apprentissage
WO2013186739A2 (fr) * 2012-06-13 2013-12-19 Ozkan Aydin Dispositif de changement de position ayant un moment variable
EP2896464B1 (fr) * 2014-01-21 2016-07-06 ABI Anlagentechnik-Baumaschinen-Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH Oscillateur
RU206076U1 (ru) * 2021-05-04 2021-08-19 Федеральное государственное бюджетное образовательное учреждение высшего образования "Кубанский государственный технологический университет" (ФГБОУ ВО "КубГТУ") Рекуператор транспортного средства с упругими элементами

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FR1093952A (fr) * 1950-05-08 1955-05-11 Schenck Gmbh Carl Vibrateur
US3433311A (en) * 1967-05-31 1969-03-18 Lebelle Jean L Pile driver and extractor with rotating eccentric masses of variable weights
FR1566358A (fr) * 1968-02-09 1969-05-09
SE350087B (fr) * 1972-01-27 1972-10-16 Vibro Verken Ab
US4113034A (en) * 1977-06-20 1978-09-12 Raygo, Inc. Uniaxial variable vibratory force generator
US5177386A (en) * 1990-08-30 1993-01-05 Kencho Kobe Co., Ltd. Vibration generator adjustable during operation
FR2679156B1 (fr) * 1991-07-15 1993-10-29 Procedes Techniques Construction Vibrateur a moment variable utilisable notamment a l'enfoncement d'objets dans le sol.
FR2692523B1 (fr) * 1992-06-19 1994-10-07 Procedes Tech Construction Dispositif pour la commande d'un vibrateur à moment variable.
DE19639789A1 (de) * 1996-09-27 1998-04-02 Univ Freiberg Bergakademie Mechanisches Vibrationssystem mit paarweise gegenläufig rotierenden Unwuchtmassen
FR2772805B1 (fr) * 1997-12-24 2000-02-25 Procedes Tech Const Dispositif pour la commande asservie de l'amplitude des vibrations d'un vibrateur a moment variable
NL1008635C2 (nl) * 1998-03-19 1999-09-21 Ice B V Trilinrichting en werkwijze voor het trillend aandrijven van een voorwerp.
WO1999058258A1 (fr) * 1998-05-08 1999-11-18 GEDIB Ingenieurbüro und Innovationsberatung GmbH Dispositif de reglage pour regler le moment statique resultant de generateurs de vibrations a balourd
DE202007005283U1 (de) * 2007-03-07 2007-07-12 Abi Gmbh Schwingungserreger
DE202007006283U1 (de) 2007-05-03 2007-12-27 Sünkenberg, Bernd Stehfahrrad

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202015003475U1 (de) 2015-02-11 2016-05-12 Liebherr-Components Biberach Gmbh Rüttler
WO2016128136A1 (fr) 2015-02-11 2016-08-18 Liebherr-Components Biberach Gmbh Vibreur
EP3165290A1 (fr) 2015-11-06 2017-05-10 BAUER Maschinen GmbH Dispositif de production de vibrations et procede d'introduction de profile dans un sol
WO2017076525A1 (fr) 2015-11-06 2017-05-11 Bauer Maschinen Gmbh Générateur de vibrations et procédé d'introduction d'un objet à battre dans le sol
WO2020224918A1 (fr) 2019-05-08 2020-11-12 Liebherr-Components Biberach Gmbh Générateur de vibrations ainsi qu'engin de chantier comportant un tel générateur de vibrations
DE102019113947A1 (de) * 2019-05-08 2020-11-12 Liebherr-Components Biberach Gmbh Schwingungserzeuger sowie Baumaschine mit einem solchen Schwingungserzeuger

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EP2158976A1 (fr) 2010-03-03
US8225685B2 (en) 2012-07-24
US20100050795A1 (en) 2010-03-04

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