EP2789862B1 - Générateur de vibrations pour machines de construction - Google Patents

Générateur de vibrations pour machines de construction Download PDF

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Publication number
EP2789862B1
EP2789862B1 EP13163221.8A EP13163221A EP2789862B1 EP 2789862 B1 EP2789862 B1 EP 2789862B1 EP 13163221 A EP13163221 A EP 13163221A EP 2789862 B1 EP2789862 B1 EP 2789862B1
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EP
European Patent Office
Prior art keywords
oscillating motor
lance
shaft
imbalance
oil
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
EP13163221.8A
Other languages
German (de)
English (en)
Other versions
EP2789862A1 (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
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by ABI Anlagentechnik Baumaschinen Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH filed Critical ABI Anlagentechnik Baumaschinen Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH
Priority to EP13163221.8A priority Critical patent/EP2789862B1/fr
Priority to US14/205,488 priority patent/US20140305235A1/en
Publication of EP2789862A1 publication Critical patent/EP2789862A1/fr
Application granted granted Critical
Publication of EP2789862B1 publication Critical patent/EP2789862B1/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
    • B06B1/18—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid
    • B06B1/186—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid operating with 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
    • 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
    • B06B1/162—Making use of masses with adjustable amount of eccentricity
    • 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
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
    • E02D7/00—Methods or apparatus for placing sheet pile bulkheads, piles, mouldpipes, or other moulds
    • E02D7/18—Placing by vibrating
    • 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 pivoting motor, in particular for a vibration generator for construction machines, in particular for vibrating rams, according to the preamble of patent claim 1.
  • vibratory rams are used to bring in piles such as profiles in the ground or to pull them out of the ground.
  • the soil is excited by vibrations with a frequency above the natural frequency of the soil and thus reaches a "pseudo-liquid state".
  • By static load the pile can then be pressed into the ground.
  • the vibration is generated by pairwise counter-rotating imbalances.
  • the vibration exciters of such vibration rams are linear-acting vibration exciters whose centrifugal force is generated by rotating imbalances.
  • An essential feature of these vibration exciters is the static moment. This is a size that describes the installed imbalance.
  • the effective size of the imbalance is adjustable.
  • the static torque is adjusted by adjusting the effective unbalance of each shaft.
  • an average imbalance is rotated against two outer imbalances in order to adjust the resulting imbalance in this way. Since the internal imbalances of all shafts are interconnected via gears and the external imbalances of all shafts via gears or the shafts themselves, the relative angles between external and internal imbalances are the same on all shafts.
  • Such a trained vibration exciter is for example in the DE 20 2007 005 283 U1 disclosed.
  • the adjustment of the imbalance groups via a pivot motor, which is designed as a rotating gear shaft, wherein the adjustment is made via a tikölbeetzten rotary piston, which is rotatable relative to this within the swing motor housing.
  • a disadvantage of the above solution is that it is very expensive to produce and also takes up much space, since the rotary feedthrough builds up to the outside and is in exposed position in front of the housing.
  • the tubes are sealed with O-rings, which are subject to high wear due to the dynamic load, which is why they must be changed frequently.
  • the invention aims to remedy this situation.
  • the invention is based on the object to provide a pivot motor in particular for a vibration exciter for construction equipment, whose manufacturing and maintenance costs are reduced in particular in relation to the oil supply and also claimed a smaller space. According to the invention, this object is achieved by features of the characterizing part of patent claim 1.
  • a pivot motor is created in particular for a vibration exciter for construction machinery, whose manufacturing and maintenance is reduced in particular with respect to the oil supply and also claimed a smaller space.
  • the long shaft of the lance which is preferably designed to be elastic and is advantageously designed by attachment to the housing of the vibration exciter so that it can accommodate slight inclinations.
  • the lance is preferably rotatably mounted end with play in a fixed to the housing of the vibration exciter flange.
  • the elasticity of the lance can be increased by having a reduced diameter in the region of the shank.
  • the oil is supplied to the chambers from the outside, wherein the oil is first passed through the at least two axial channels of the lance into the region of the shaft, which is enclosed by the pivot motor housing.
  • the two channels have different lengths and open into a respective groove which encloses the lance at the level of the mouths of the holes.
  • On the shaft side opens into this groove a radial bore through which a chamber of the swing motor is supplied with oil.
  • the lance and the axial bore of the pivot motor shaft in the region of the annular grooves of the lance or preferably in the region of the pivot motor shaft, which is enclosed by the pivot motor housing, formed as a sliding bearing with very close game.
  • the narrow gap between the lateral surface of the lance and the axial bore of the pivot motor shaft serves to seal the at least two grooves against each other and with respect to the vibration exciter interior.
  • the surface of the lance is in the range of this Plain bearing preferably provided with a lubricious coating, preferably a plastic coating, which is preferably applied as a lacquer.
  • no sliding seals are present over the length of the fit between the lance and the axial bore of the swing motor shaft in the region of the annular grooves of the lance.
  • 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 an engaging in the head piece dowel pin.
  • the swivel motor is designed as a single-wing or double-wing rotary piston rotary engine.
  • Rotary piston pivot motors also referred to as rotary vane pivot motors, generate torque directly through one or more vanes disposed on the swing motor shaft, which are pressurized with hydraulic oil under pressure.
  • rotary swivel motors are referred to as single-leaf or double-leaf.
  • the swivel motor housing of the swivel motor is preferably designed as a circular segment-shaped imbalance.
  • a space-optimized imbalance is formed by the swivel motor housing itself.
  • the angle of rotation of the rotary vane of the single-pivoting pivot motor is limited by a respective stop surface of two arranged on the pivot motor housing stops, wherein between the two stops defined by the rotation angle pivot space of the rotary vane opposite at least one can be acted upon with oil oil pocket, wherein Oil supply of at least one oil pocket in addition to the supply channels of the two sides of the rotary vane pressure chambers arranged at least one separate channel is connected via an externally arranged on the lance ring groove with a opening into the at least one oil pocket supply bore of the hollow shaft.
  • the bearings with which the swivel motor housing is mounted on the swivel motor shaft increasingly loaded with increasing speed by the centrifugal force.
  • a bearing force results from the oil pressure in the chambers of the slewing motor. This resulting from centrifugal force and oil pressure in the chambers bearing load leads to an increased adjusting torque that is reduced by the provision of at least one oil bag.
  • the arrangement of a separate channel for oil supply to the oil pocket, a hydraulic short circuit between the two chambers of the swing motor is excluded.
  • two check valves or a shuttle valve may be arranged. Valves, however, are sensitive to dynamic loads, which are essential in a vibrator gearbox.
  • the maximum pivot angle of the rotary wing is less than 180 °, preferably less than 160 °, preferably 150 ° or less.
  • the largest possible imbalance is possible with low mass of the swivel motor housing.
  • swivel angle of 180 ° further results in the advantage that a provided for reducing the bearing force oil pocket over the circumference of the swing motor housing can be made longer.
  • an equally longer sealing distance between oil pocket and chambers of the swing motor can be formed.
  • the wing can be made higher, which at the same required adjusting torque and the same length of the chambers of the swing motor in the axial direction a lower required Pressure results. Accordingly, the resulting from the oil pressure in the chambers of the swing motor, the bearing load-increasing force component is reduced.
  • the invention further relates to a vibration exciter for construction machines, in particular vibratory rams, with at least one axis with at least two imbalance masses, in which a pivot motor of the aforementioned type for adjusting the rotational position of at least one imbalance mass is arranged.
  • a pivot motor of the aforementioned type for adjusting the rotational position of at least one imbalance mass is arranged.
  • the pivot motor shaft is arranged rotatably to this, a significant reduction of the required installation space is achieved, in particular, no separate shaft for a phase shifter is required.
  • three unbalanced masses are arranged on at least one axis, the average imbalance mass formed by the circular segment-shaped pivot motor housing of the swivel motor, whose hollow shaft is part of the axis.
  • the selected as an exemplary vibration exciter is designed as a three-shaft vibrator gear.
  • a swivel motor 5 designed as a rotary swivel motor is arranged between the toothed wheels 4, the swivel motor shaft 51 of which is part of the axle 2.
  • the central imbalance shaft 1 ' has on its axis 2 between the gears 4 an inner imbalance mass 3'.
  • the imbalance mass 3 ' is dimensioned twice as wide as the outer imbalance masses. 3
  • the imbalance masses 3, 3 ' are formed in a circular sector.
  • the radius of the outer unbalance 3 of the outer unbalanced shafts 1 substantially corresponds to the radius of the gears 4.
  • the radius of the outer imbalances 3 and the inner imbalance 3 'of the central imbalance shaft 3' is significantly greater than the radius of the gears 4 of the central imbalance shaft 1 ', which are larger in size than the gears 4 of the outer unbalanced shafts 1, between which a rotary piston pivot motor 5 is arranged.
  • the rotary piston pivoting motor 5 is formed by a pivot motor shaft 51, which is part of the axis 2, and arranged on the pivot motor shaft 51 pivot motor housing 55.
  • the swing motor shaft is provided in the exemplary embodiment with an axial bore 511, spaced from each other, two radial bores 512 led to the outside are.
  • a rotary vane 52 is formed on the pivot motor shaft 51, which is arranged within the pivot space 55 formed by the inner contour 54 of the pivot motor housing 53.
  • the pivot motor housing 53 is formed according to the imbalance masses 3, 3 'as a sector-shaped unbalance.
  • the pivot space 55 formed between the inner contour 54 of the pivot motor housing 53 and the pivot motor shaft 51 is limited by two stop surfaces 56, which allow a maximum rotation angle of 150 degrees.
  • two chambers 57 are formed for the operation of the rotary piston pivot motor 5.
  • a lance 6 for supplying the chambers 57 of the rotary piston pivot motor 5 is introduced with hydraulic oil.
  • the lance 6 is substantially cylindrical.
  • the lance 6 has a head piece 61, which is adjoined by a shaft 62, which merges into a diameter-enlarged slide bearing portion 63.
  • two channels 64 are provided coaxially to the central axis 11 for supplying the chambers 57 of the rotary piston pivot motor 5.
  • the channels 64 each open into an annular groove 65 arranged within the sliding bearing section 63, which is arranged such that one of the radial bores 512 is arranged as a pivoting motor 51 orthogonal thereto, which axial bore 511 connects to the respective chamber 57 of the rotary piston pivoting motor 5 represents.
  • the lance 6 is mounted with its head piece 61 on a flange 7, which is fixed to the - not shown - housing of the vibrator gear.
  • the flange part 7 consists essentially of a base plate 71, which is connected centrally with a cup-shaped recess 72 which is aligned with a bore 73 guided through the base plate 71.
  • the cup-shaped recess 72 receives the lid part 75, which is provided with a centrally arranged cylindrically shaped recess 76 whose outer diameter is slightly larger than the outer diameter of the head piece 61 of the lance 6.
  • the cover part 75 is provided with supply connections 77 for supplying the channels 64 the lance 6 received by the lid part 75 is provided.
  • a dowel pin 78 is arranged for engagement in an eccentrically arranged in the head piece of the lance 6 fitting hole 66.
  • Surrounding the recess 72 of the cover part 75 are parallel to each other two annular grooves for receiving an O-ring 8 is introduced.
  • the O-ring 8 bridges the gap between the head piece 61 of the lance 6 and the recess 76 of the cover part 75, whereby the head piece 61 is mounted slightly pivotable in the cover part 75.
  • the cover part 75 is fixed in the recess 72 of the base plate 71 and receives the head piece 61 of the lance 6, whose shaft 62 projects through the bore 73 of the base plate into the axial bore 511 of the pivot motor shaft 51 of the rotary piston pivot motor 5.
  • the cover part 75 is sealed relative to the cup-shaped recess 76 by means of an O-ring 81.
  • the vibrator is operated by two - not shown - drives that drive the top and bottom unbalance shaft 1, which are identical to the pivot motor shafts 51 of the rotary piston pivot motor 5 here.
  • the entire static moment of the upper and lower imbalance shaft 1 corresponds to the static moment of the middle imbalance shaft 1 in this three-shaft vibrator Therefore, the imbalance 3 on the lower and upper imbalance shaft 1 does not claim the available space.
  • each have a rotary piston pivot motor 5 is integrated, which is located in each case in the middle imbalance.
  • the pivot motor housing 53 of the rotary piston pivoting motor 5 is formed as a circular segment unbalanced mass and rotatably mounted on the respective unbalanced shaft 1.
  • the angle of rotation is limited by the integrally formed on the pivot motor shaft 51 rotary vane 52 in interaction with the abutment surfaces 56 of the pivot space 55 to a maximum of 150 degrees.
  • the rotary vane 52 also serves as a seal between the two chambers 57 which are delimited between the rotary vane 52 and the pivot motor housing 53 and the pivot motor shaft 51.
  • the two chambers 57 are supplied with hydraulic oil, which is supplied via the radial bores 512 of the swing motor shaft 51.
  • the fixed lance 6 is mounted in the central, axially extending bore 511. The sealing effect is achieved through narrow gaps.
  • the hydraulic transmission is equipped with two rotary actuators, which ensures low pressure operation while ensuring the required maximum torque of the swing motors.
  • the hydraulic oil is supplied through the supply ports 77 to the channels 64 of the lance 6. From these channels 64, the oil enters the annular grooves 65 on the outside of the lance.
  • the chambers 57 of the rotary piston pivot motor 5 are connected by radial bores 512, which connect the respective annular groove space with the corresponding chamber 57.
  • a Leckageringnut 67 is disposed between the two annular grooves 65, which serves to dissipate occurring leak oil.
  • the fit between the lance 6 and the axial bore 511 of the pivot motor shaft 51 is designed in the region of the annular grooves 65, 67 as a narrow slide bearing.
  • the lance is provided with a sliding bearing coating made of plastic. Due to the sliding bearing formed between the axial bore 511 of the pivot motor shaft 51 and the sliding bearing portion 63 of the lance 6, some leakage occurs, but at the same time lubricates the bearing, separates the surfaces and thereby counteracts wear.
  • the pivot motor housing 53 of the rotary vane pivot motor 5 is formed in each case as imbalance, the bearings with which the pivot motor housing 53 is mounted on the pivot motor shaft 51, with increasing speed increasingly burdened by centrifugal force.
  • a bearing force results from the oil pressure in the chambers 57.
  • an oil pocket 58 which can be acted upon by oil pressure, can additionally be introduced into the swivel motor housing 53 (cf. FIG. 11 ). This oil pressure can be diverted, for example, in the control of the chambers 57.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Paleontology (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Hydraulic Motors (AREA)

Claims (14)

  1. Moteur pivotant destiné notamment à un générateur de vibrations pour machines de construction, comprenant un carter de moteur pivotant agencé sur une arbre de moteur pivotant de façon à pouvoir tourner, sachant qu'au moins deux chambres sont agencées pour les mettre sous pression avec une huile hydraulique via laquelle il est possible d'exploiter le moteur pivotant, caractérisé en ce que l'arbre (51) de moteur pivotant est doté d'un alésage axial (511) dans lequel fait saillie une lance (6) agencée de façon à ne pas pouvoir tourner, dans laquelle sont disposés axialement au moins deux canaux (64) servant à alimenter le moteur pivotant (5) en huile, qui aboutissent dans des gorges annulaires (65) installées à l'extérieur contre la lance (6) au moins partiellement sur la périphérie, sachant que dans l'arbre (51) de moteur pivotant se trouvent des alésages radiaux (512) pour relier au moins deux des gorges annulaires (65) de la lance (6) avec au moins deux chambres sous pression (57), sachant que l'ajustage entre la lance (6) et l'alésage axial (511) de l'arbre (51) de moteur pivotant est exécuté sous forme de palier lisse étroit dans la zone des gorges annulaires (65) de la lance (6).
  2. Moteur pivotant selon la revendication 1, caractérisé en ce que la lance (6) est munie, dans la zone des gorges annulaires (65), d'un revêtement en matière synthétique constitué de préférence de téflon.
  3. Moteur pivotant selon l'une des revendications 1 et 2, caractérisé en ce que la lance (6) présente une diminution de diamètre dans la zone de la tige (62), ce qui accroît l'élasticité.
  4. Moteur pivotant selon l'une des revendications 1 à 3, caractérisé en ce que l'extrémité de la lance (6) repose avec du jeu dans une pièce (7) officiant de flasque.
  5. Moteur pivotant selon la revendication 4, caractérisé en ce que la lance (6) présente à l'extrémité une pièce têtière (61) d'un diamètre accru avec laquelle elle repose en appui dans la pièce (7) officiant de flasque.
  6. Moteur pivotant selon la revendication 4 ou 5, caractérisé en ce que l'interstice formé par le jeu entre la lance (6) et la pièce (7) officiant de flasque (7) est ponté avec au moins un joint torique (8).
  7. Moteur pivotant selon la revendication 6, caractérisé en ce que la sécurité antirotation est obtenue grâce au moins à une clavette (78) axiale faisant saillie de manière excentrée dans la lance (6).
  8. Moteur pivotant selon l'une des revendications précédentes, caractérisé en ce qu'aucun joint n'est disposé pour étanchéiser le carter (53) de moteur pivotant par rapport à l'arbre (51) de moteur pivotant, sachant que l'effet étanchéisant est obtenu exclusivement via la cote intersticielle.
  9. Moteur pivotant selon l'une des revendications 2 à 8, caractérisé en ce qu'aucun joint frottant n'est prévu sur la longueur de l'ajustage entre la lance (6) et l'alésage axial (511) de l'arbre (51) de moteur pivotant dans la zone des gorges annulaires (65) de la lance (6).
  10. Moteur pivotant selon la revendication 9, caractérisé en ce que le moteur pivotant est un moteur pivotant à piston rotatif mono-ailette ou bi-ailette.
  11. Moteur pivotant selon l'une des revendications précédentes, caractérisé en ce que le carter (53) de moteur pivotant est configuré en masselotte en forme d'arc de cercle, sachant que le moteur pivotant (5) est configuré mono-ailette.
  12. Moteur pivotant selon la revendication 11, caractérisé en ce que l'angle de rotation de l'ailette rotative (52) est limité par deux surfaces butées (56) agencées contre le carter (53) de moteur pivotant, sachant qu'entre les deux surfaces butées (56) - en face de l'espace de pivotement (55) de l'ailette rotative (52) défini par l'angle de rotation - est formée au moins une poche (58) pouvant être mise sous pression d'huile, sachant que pour alimenter au moins cette poche (58) en huile au moins un canal séparé est agencé en plus des canaux chargés d'alimenter les chambres (57) situées des deux côtés de l'ailette rotative (52), ledit canal étant relié, via une gorge annulaire (67) agencée à l'extérieur contre la lance, à un alésage d'alimentation de l'arbre creux débouchant dans au moins une poche d'huile (58).
  13. Générateur de vibrations pour machines de construction, en particulier pour vibrofonceurs, comprenant au moins une axe équipé d'au moins deux masselottes, caractérisé en ce qu'un moteur pivotant (5) selon l'une des revendications précédentes est agencé pour modifier la position rotative d'au moins une masselotte.
  14. Générateur de vibrations selon la revendication 13, caractérisé en ce que trois masselottes sont agencées sur au moins un axe, en ce que la masselotte médiane du générateur est formée par le carter (53) du moteur pivotant (5) selon la revendication 11 ou 12, dont l'arbre (51) de moteur pivotant fait partie intégrante de l'axe.
EP13163221.8A 2013-04-10 2013-04-10 Générateur de vibrations pour machines de construction Active EP2789862B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP13163221.8A EP2789862B1 (fr) 2013-04-10 2013-04-10 Générateur de vibrations pour machines de construction
US14/205,488 US20140305235A1 (en) 2013-04-10 2014-03-12 Vibration exciter for construction machines

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Application Number Priority Date Filing Date Title
EP13163221.8A EP2789862B1 (fr) 2013-04-10 2013-04-10 Générateur de vibrations pour machines de construction

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EP2789862A1 EP2789862A1 (fr) 2014-10-15
EP2789862B1 true EP2789862B1 (fr) 2015-11-04

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EP2789403B1 (fr) * 2013-04-10 2015-12-16 ABI Anlagentechnik-Baumaschinen-Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH Générateur de vibrations pour machines de construction
US9941779B2 (en) * 2015-05-08 2018-04-10 Dynamic Structures And Materials, Llc Linear or rotary actuator using electromagnetic driven hammer as prime mover
CN104841630A (zh) * 2015-05-20 2015-08-19 广州华宝矿山设备有限公司 一种振动筛新型激振器
CN108397448B (zh) * 2018-04-23 2019-12-20 浙江大学宁波理工学院 双联阀负载独立控制式电液激振器及其电液激振装置和偏置控制方法

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