EP2789402B1 - Accélérateur d'oscillations - Google Patents

Accélérateur d'oscillations Download PDF

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Publication number
EP2789402B1
EP2789402B1 EP13163222.6A EP13163222A EP2789402B1 EP 2789402 B1 EP2789402 B1 EP 2789402B1 EP 13163222 A EP13163222 A EP 13163222A EP 2789402 B1 EP2789402 B1 EP 2789402B1
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EP
European Patent Office
Prior art keywords
swivel motor
lance
vibration generator
generator according
swivel
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
EP13163222.6A
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German (de)
English (en)
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EP2789402A1 (fr
Inventor
Albrecht Dr. Ing. Kleibl
Christian Heichel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ABI Anlagentechnik Baumaschinen Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH
Original Assignee
ABI Anlagentechnik Baumaschinen Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH
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Application filed by ABI Anlagentechnik Baumaschinen Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH filed Critical ABI Anlagentechnik Baumaschinen Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH
Priority to EP13163222.6A priority Critical patent/EP2789402B1/fr
Priority to US14/189,017 priority patent/US20140305234A1/en
Publication of EP2789402A1 publication Critical patent/EP2789402A1/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
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/12—Characterised by the construction of the motor unit of the oscillating-vane or curved-cylinder type
    • 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 vibration exciter, in particular for a vibrating hammer, according to the preamble of patent claim 1.
  • vibration generators such as vibrators, vibrators or vibratory bears are used to bring profiles into the soil or to pull or to compact soil material.
  • the soil is stimulated by vibration and thus reaches a "pseudo-liquid" state.
  • the vibration is characterized by a linear movement and is generated by pairwise counter-rotating imbalances within a Vibratorgetriebes.
  • Vibration generators are characterized by the installed unbalance, the so-called "static moment".
  • the amplitude, frequency or force direction of the vibrator In order to achieve optimal propulsion or good compaction depending on the pile material and soil properties, it is desirable to control the amplitude, frequency or force direction of the vibrator.
  • the adjustment of the vibration is expediently via a change of the static torque or the phase position of the imbalances.
  • To adjust the effective size of the unbalance waves with fixed imbalances are rotated against each other, or the active imbalance of each wave is changed.
  • a special design is Hochkantvibratoren. These are usually equipped with three or four unbalanced shafts.
  • the adjustment of the static torque of the vibrator is done by adjusting the effective unbalance of each wave. In this case, an average unbalance is regularly rotated against two outer imbalances to adjust in this way the resulting imbalance.
  • the invention aims to remedy this situation.
  • the invention has for its object to provide a vibration generator, the variety of parts is reduced and are avoided in the restrictions of the maximum torque of the swing motor. According to the invention, this object is solved by the features of the characterizing part of patent claim 1.
  • the variety of parts is reduced and are avoided in the limitations of the maximum torque. Due to the fact that the swivel motor is arranged axially such that it is positioned outside the areas swept by the imbalances, only the swivel motor shaft is located in the area between the imbalances, which is why the imbalances can be carried out at the same center distance with a larger outside diameter. Similarly, the outer diameter of the swing motor is not limited by adjacent imbalances. The inventive arrangement of the swing motor now only two rows of gears are required, whereby the variety of parts is reduced.
  • At least one of the shafts arranged parallel to one another and, in addition, the swivel motor shaft of the swivel motor or the swivel motor housing of the swivel motor are connected to a drive.
  • the drive motor, the shaft end of the swing motor rotates, drives via the mounted on the swing motor shaft gear a number of gears, which is connected to the respective average imbalance of each shaft.
  • the drive torque is transmitted to the imbalance via this shaft, but the pivot mechanism of the swing motor is not in the power flow of the drive torque. The same effect occurs when the swing motor housing is driven by the drive motor.
  • At least one of the drives is designed as a hydraulic motor with adjustable displacement. This makes it possible to influence the size and direction of the torque to be transmitted by the swivel motor by changing the ratio of the absorption volumes of the motors driving the two imbalance groups, whereby the swivel motor can be assisted or braked in its swiveling motion.
  • the swivel motor is a rotary-wing pivoting motor, which is preferably designed as a single-wing and has a swivel angle greater than 210 degrees, preferably greater than 240 degrees, particularly preferably greater than 270 degrees.
  • a considerably larger pivot angle is provided to rotate the imbalances 180 degrees against each other.
  • an increase of the torque is made possible via a gear ratio, wherein a better utilization of the space is effected.
  • the swivel motor shaft and the swivel motor housing are each provided with at least one gear, which engages in each case in a gear connected to one of the waves unbalanced mass.
  • the at least one arranged on the pivot motor shaft gear has a smaller diameter than that with this gear engaged, connected to an imbalance mass gear.
  • no seals are arranged for sealing the swivel motor housing relative to the swivel motor shaft of the at least one swivel motor, the sealing effect being effected exclusively via the gap dimension.
  • the swivel motor shaft of the swivel motor is provided with an axial bore into which projects a fixed lance having at least two channels for oil supply of the swivel motor, which open into a respective outside of the lance arranged annular groove, wherein in the swing motor shaft radial Holes for connecting the at least two annular grooves of the lance are introduced with the chambers to be supplied.
  • the fit between the lance and the shaft bore in the region of the annular grooves is preferably designed as a narrow slide bearing.
  • the lance is preferably coated in this area with plastic.
  • the fixed arranged lance compensates for the dancing movements of the pivot bearing shaft in the functionally bearing a game bearing bearings. This is done on the one hand by the long shaft of the lance, which is preferably elastic and is advantageously designed by attachment to the flange so that they light Can accommodate inclinations.
  • the lance is preferably rotatably mounted end with play in a located on the housing of the vibration exciter flange.
  • the lance has at its end an enlarged diameter head piece, with which it is mounted in the flange.
  • a resilient attachment of the lance is made possible in the flange.
  • the gap formed by the play between the lance and the flange part is preferably bridged by at least one O-ring. Against rotation, the lance can be secured by means of a pin engaging in the head piece.
  • the selected as an exemplary vibration exciter is designed as a four-shaft vibrator gear.
  • There are four imbalance shafts 1 are arranged on the spaced apart two outer imbalance masses 11 are attached.
  • an average imbalance mass 12 is arranged, which is connected to a gear 121.
  • another gear 13 is mounted on the imbalance shaft 1 at its end facing the swivel motor 2.
  • the imbalance shafts 1 are arranged parallel to one another in such a way that the toothed wheels 121, 13 of two imbalance shafts 1 are engaged with one another so that two imbalance shaft groups 10 are formed.
  • the two imbalance shaft groups 10 are coupled to each other via the gears 211, 221 of a swing motor 2.
  • the swivel motor 2 comprises a swivel motor shaft 21 and a swivel motor housing 22, wherein the rotational position of the swivel motor housing 22 is variable relative to the swivel motor shaft 21.
  • a wing 23 is formed, which is rotatable within the pivot motor housing 22.
  • a stop 24 is formed, by which the pivot angle of the wing 23 is limited. Between the stop 24 and the wing 23 on both sides of the wing 23 each have a chamber 25 is limited.
  • a gear 211 is fixed, which is in each case with a gear 121 of a central unbalanced mass 12 of an unbalanced shaft 1 of an unbalanced shaft group 10 is engaged.
  • a gear 221 is arranged on the swivel motor housing 22 of the swivel motor 2, which is in engagement with a gearwheel 13 of an imbalance shaft 1 of an imbalance shaft group 10.
  • the swivel motor 2 is arranged with its swivel motor housing 22 and arranged in this rotatably mounted on the pivot motor shaft 21 wing 23 axially offset so that it is outside of the unbalanced masses 11, 12 swept areas.
  • the gear 211 facing the end of the swing motor shaft 21 is driven by a hydraulic motor.
  • a conventional toothed shaft adapter is used as a coupling between the - not shown - toothed shaft of the hydraulic motor 3 and the swing motor shaft 21.
  • the diameter of the pivot motor shaft 21 is significantly larger than in a conventional swing motor as he, for example, in the DE 20 2007 005 283 U1 is used, chosen.
  • the assembly of the swivel motor 2 is performed by the hydraulic motor 3 opposite end of the swing motor shaft 21.
  • the two outer unbalanced shafts 1 of the vibrator gear are also connected to a hydraulic motor 31.
  • the hydraulic motor 3 which drives the swing motor 2 is a constant motor; in the hydraulic motors 31 are hydraulic motors with adjustable displacement.
  • the displacement of the two hydraulic motors 31 with adjustable displacement can be set exactly be that the swing motor 2 transmits no drive torque.
  • the gears 211, 221 of the swing motor 2 are formed smaller than the gears 121, 13 of the unbalanced shafts 1.
  • the swing motor 2 is formed such that the wing 23 has a pivot angle of 280 degrees within the swing motor housing 22.
  • the translation of the gears 211, 221 of the swing motor 2 to the gears 121, 13 of the unbalanced shafts 1 is selected such that a rotation of the pivot motor housing 22 with the arranged thereon gear 221 by 280 degrees relative to the pivot motor shaft 21, a relative rotation of the unbalanced shafts 1 attached gears 13 to the arranged on the central imbalance masses 12 gears 121 of 180 degrees.
  • the hydraulic motor 3 which rotates the swing motor shaft 21 drives a series of gears 121 via the gear 211 closest to the hydraulic motor 3 mounted on the swing motor shaft 21 and connected to each unbalanced mass 12 of each unbalanced shaft 1.
  • the hydraulic motor 3 drives the pivot motor shaft 21 and the drive torque is transmitted to the imbalance 12 via this pivot motor shaft 21;
  • the pivot mechanism of the swing motor 2 is not in the power flow of the drive torque.
  • the two other, external hydraulic motors 31 drive the outer imbalance masses 11 of each imbalance shaft 1, which are connected to each other via the gears 13.
  • the present vibratory transmission is distinguished from the prior art vibrators in that the gear trains are significantly shortened. If the powers to be transmitted of all gear pairings are added up, the result for the present vibrator gearbox is the smallest sum. This results in lower mechanical losses and less noise.
  • the swivel motor shaft 21 of the swivel motor 3 is provided in the exemplary embodiment with an axial bore 212, from which two radial bores 213 spaced from one another are guided to the outside.
  • a lance 4 for supplying the chambers 25 of the formed as a rotary piston rotary engine pivot motor 2 is introduced with hydraulic oil.
  • the lance 4 is substantially cylindrical.
  • the lance 4 has a head piece 41, to which a shaft 42 adjoins, which merges into a diameter-enlarged sliding bearing portion 43.
  • two channels 44 for supplying the chambers 25 of the swing motor 2 are introduced.
  • the channels 44 respectively open into an annular groove 45 disposed within the sliding bearing section 43, which is arranged such that one of the radial bores 213 of the pivot motor shaft 21 is arranged orthogonal to this, which axial borehole 212 forms the connection to the respective chamber 25 of the pivoting motor 2.
  • the lance 4 is mounted with its head 41 to a flange 5, which is fastened by screws 54 on the - not shown - housing of the vibrator gear.
  • the flange part 5 consists essentially of a base plate 51, which is centrally provided with a cup-shaped recess 52 which is aligned with a guided through the base plate 51 bore 53.
  • the cup-shaped formation 52 accommodates the lid part 55, which is provided with a centrally arranged, cylindrically shaped recess 56 whose outer diameter is slightly larger than the outer diameter of the head piece 41 of the lance 4th
  • the cover part 55 is provided with supply connections 57 for supplying the ducts 44 of the lance 4 received by the cover part 55. Furthermore, a dowel pin 58 is arranged in the recess 56 of the cover part 55 for engagement in an eccentric arranged in the head piece 41 of the lance 4 fitting bore 46. Surrounding the recess 52 of the cover member 55 are parallel to each other two annular grooves 59 for receiving a respective O-ring 6 is introduced. The O-rings 6 bridge the gap between the head piece 41 of the lance 4 and the recess 56 of the cover part 55, whereby the head piece 41 is mounted slightly pivotable in the cover part 55.
  • the cover part 55 is fixed in the recess 52 of the base plate 51 and receives the head 41 of the lance 4, the shaft 42 protrudes through the bore 53 of the base plate into the axial bore 212 of the swing motor shaft 21 of the swing motor 2.
  • the cover part 55 is sealed relative to the cup-shaped recess 56 by means of an O-ring 61.
  • the angle of rotation is limited by the integrally formed on the pivot motor shaft 21 wings in interaction with the stop 24.
  • the vane 23 simultaneously serves as a seal between the two chambers 25, which are delimited between the vane 23 and the pivot motor housing 22 and the pivot motor shaft 21.
  • the two chambers 25 are supplied with hydraulic oil, which is supplied via the radial bores 213 of the swing motor shaft 21.
  • the fixed lance 4 is mounted in the central, axially extending bore 212. The sealing effect is achieved through narrow gaps.
  • the hydraulic oil is supplied through the supply ports 57 to the channels 44 of the lance 4. From these channels 44, the oil enters the annular grooves 45 on the outside of the lance.
  • the chambers 25 of the swing motor 2 are connected by the radial bores 213 which connect the respective annular groove space with the corresponding chamber 25.
  • a Leckageringnut 47 is disposed between the two annular grooves 45, which serves to dissipate occurring leak oil.
  • the fit between the lance 4 and the axial bore 212 of the pivot motor shaft 21 is designed in the region of the annular grooves 45, 47 as a narrow slide bearing.
  • the lance 4 is provided with a sliding bearing coating made of plastic. Due to the between the axial bore 212 of the pivot motor shaft 21 and the sliding bearing portion 43 of the lance 4 certain slide bearing exits a certain leakage, but at the same time lubricates the bearing, the surfaces separates and thereby counteracts wear.

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

Claims (12)

  1. Accélérateur d'oscillations, notamment pour un pilon de vibrations, comprenant au moins deux arbres disposés en parallèle l'un relativement à l'autre, ainsi qu'au moins deux masses de balourd (11, 12) fixées sur l'un ou l'autre de plusieurs arbres, un moteur pivotant (2) étant agencé pour le réglage de la position de rotation relative des masses de balourd (11, 12) l'une relativement à l'autre, comprenant un arbre (21) à moteur pivotant et un carter (22) de moteur pivotant, l'arbre (21) à moteur pivotant faisant partie de l'un des arbres et la position de rotation du carter (22) du moteur pivotant étant modifiable relativement à l'arbre (21) à moteur pivotant, le moteur pivotant (2) étant agencé axialement rapporté de sorte à ce qu'il soit disposé en dehors des zones couvertes par les masses de balourd (11, 12), caractérisé en ce qu'au moins l'un des arbres agencés en parallèle l'un envers l'autre est relié à un entraînement (31) ainsi qu'en plus, l'arbre à moteur pivotant (21) du moteur pivotant (2) ou le carter (22) du moteur pivotant du moteur pivotant (2) est relié à un entraînement supplémentaire.
  2. Accélérateur d'oscillations selon la revendication 1, caractérisé en ce qu'au moins l'un des entraînements (3, 31) est réalisé en tant que moteur hydraulique ayant un volume d'absorption réglable.
  3. Accélérateur d'oscillations selon l'une des revendications 1 et 2, caractérisé en ce que le moteur pivotant (2) est un moteur pivotant à voilure tournante.
  4. Accélérateur d'oscillations selon la revendication 3, caractérisé en ce que le moteur pivotant (2) est réalisé à une voilure et présente un angle d'oscillation supérieur à 210°, préférentiellement supérieur à 240°, plus préférentiellement supérieur à 270°.
  5. Accélérateur d'oscillations selon la revendication 4, caractérisé en ce que l'arbre à moteur (21) ainsi que le carter (22) de moteur pivotant sont chacun munis d'au moins une roue dentée (211, 221) qui s'engrène chacune dans une roue dentée (121, 13) reliée à l'une des masses de balourd (11, 12) agencée sur l'un des arbres (1).
  6. Accélérateur d'oscillations selon la revendication 5, caractérisé en ce que l'une au moins des roues dentées (211) agencée sur l'arbre (21) à moteur pivotant présente un diamètre inférieur que la roue dentée (121) reliée à une masse de balourd (12) et engrenée dans cette roue dentée (221).
  7. Accélérateur d'oscillations selon l'une des revendications précédents, caractérisé en ce qu'aucun joint n'est disposé pour l'étanchement du carter (22) du moteur pivotant en face de l'arbre (21) du moteur pivotant du moteur pivotant (2), l'effet d'étanchement étant assuré exclusivement via la dimension de la fente.
  8. Accélérateur d'oscillations selon la revendication 7, caractérisé en ce que l'arbre (21) à moteur pivotant du moteur pivotant (2) est muni d'un alésage axial (212) dans lequel fait saillie une lance (4) immobile qui présente au moins deux canaux (44) pour l'alimentation en huile du moteur pivotant (2) qui débouchent chacun dans une rainure annulaire (45) agencée à l'extérieur de la lance (4), des alésages radiaux (213) étant pratiqués dans l'arbre à moteur pivotant (21) afin de relier les au moins deux rainures annulaires (45) de la lance (4) aux chambres (25) à alimenter du moteur pivotant (2).
  9. Accélérateur d'oscillations selon la revendication 8, caractérisé en ce que le calage entre la lance (4) et l'alésage axial (212) de l'arbre (21) à moteur pivotant est réalisé en tant que palier à glissement étroit dans la zone des rainures annulaires (45).
  10. Accélérateur d'oscillations selon la revendication 8 ou 9, caractérisé en ce qu'à son extrémité, la lance (4) est montée anti-rotulant et avec un jeu à une partie de bride (5) fixée sur le boîtier de l'accélérateur d'oscillations.
  11. Accélérateur d'oscillations selon la revendication 10, caractérisé en ce qu'à son extrémité, la lance (4) présente une pièce de tête (41) à diamètre agrandi avec laquelle elle est montée dans la partie de bride (5).
  12. Accélérateur d'oscillations selon la revendication 10 ou 11, caractérisé en ce que la fente formée entre la lance (4) et la partie de bride (5) en raison du jeu est compensée par au moins un joint torique (6).
EP13163222.6A 2013-04-10 2013-04-10 Accélérateur d'oscillations Active EP2789402B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP13163222.6A EP2789402B1 (fr) 2013-04-10 2013-04-10 Accélérateur d'oscillations
US14/189,017 US20140305234A1 (en) 2013-04-10 2014-02-25 Vibration exciter

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP13163222.6A EP2789402B1 (fr) 2013-04-10 2013-04-10 Accélérateur d'oscillations

Publications (2)

Publication Number Publication Date
EP2789402A1 EP2789402A1 (fr) 2014-10-15
EP2789402B1 true EP2789402B1 (fr) 2017-05-17

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EP (1) EP2789402B1 (fr)

Families Citing this family (7)

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Publication number Priority date Publication date Assignee Title
EP2789403B1 (fr) * 2013-04-10 2015-12-16 ABI Anlagentechnik-Baumaschinen-Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH Générateur de vibrations pour machines de construction
DE102013020690A1 (de) * 2013-12-03 2015-06-03 Bomag Gmbh Schwingungserreger für einen Vibrationsverdichter sowie Baumaschine mit einem solchen Schwingungserreger
US9941779B2 (en) * 2015-05-08 2018-04-10 Dynamic Structures And Materials, Llc Linear or rotary actuator using electromagnetic driven hammer as prime mover
EP3165290B1 (fr) 2015-11-06 2021-04-07 BAUER Maschinen GmbH Dispositif de production de vibrations et procede d'introduction de profile dans un sol
CN105537092B (zh) * 2015-12-08 2018-10-12 中航勘察设计研究院有限公司 机械式激振器及采用该激振器的扭转测试激振设备
DE102017122371A1 (de) * 2017-09-27 2019-03-28 Hamm Ag Verdichterwalze
DE102019113947A1 (de) * 2019-05-08 2020-11-12 Liebherr-Components Biberach Gmbh Schwingungserzeuger sowie Baumaschine mit einem solchen Schwingungserzeuger

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