EP0524056B1 - Schwingungserreger mit einstellbarer Unwucht, insbesondere zum Eintreiben von Gegenständen in den Boden - Google Patents

Schwingungserreger mit einstellbarer Unwucht, insbesondere zum Eintreiben von Gegenständen in den Boden Download PDF

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Publication number
EP0524056B1
EP0524056B1 EP92401960A EP92401960A EP0524056B1 EP 0524056 B1 EP0524056 B1 EP 0524056B1 EP 92401960 A EP92401960 A EP 92401960A EP 92401960 A EP92401960 A EP 92401960A EP 0524056 B1 EP0524056 B1 EP 0524056B1
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EP
European Patent Office
Prior art keywords
vibrator
phase
shifter
hydraulic
vibrator according
Prior art date
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Expired - Lifetime
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EP92401960A
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English (en)
French (fr)
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EP0524056A1 (de
Inventor
Christian Houze
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PTC
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Procedes Techniques de Construction
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Classifications

    • 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
    • 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
    • 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
    • Y10T74/19—Gearing
    • Y10T74/1956—Adjustable

Definitions

  • the present invention relates to a variable moment vibrator which can be used in particular, but not exclusively, for driving objects, such as piles or sheet piles, into the ground.
  • the vibrators commonly used in this kind of application involve at least a couple of rotary flyweights eccentric with respect to their drive axis and means making it possible to drive in rotation at the same speed. but in opposite direction the two drive axes.
  • variable speed drive means generally hydraulic motors
  • these variable speed drive means are bulky, often too expensive and even too fragile so that in practice this solution is not used.
  • the mechanical coupling finger / groove used is not suitable for the production of a vibrator, because of the very small dimensions of the contact surfaces between the finger and the groove. For this reason, the phase shifter will not withstand the vibrations produced by the vibrator.
  • Another disadvantage of the known systems consists in that they do not make it possible to adapt the vibratory power transmitted both to the working conditions of the tool to which the vibrations are applied and to the characteristics of the power source.
  • the purpose of the drawback is therefore more particularly to eliminate these drawbacks.
  • the vibrator involves at least two trains of eccentric weights each comprising at least two eccentric weights rotatably mounted around shafts integral with two respective pinions which mesh with each other so as to rotate in direction reverse with respect to each other, thanks to a motorization comprising a first motor and a transmission device including a phase shifter.
  • a motorization comprising a first motor and a transmission device including a phase shifter.
  • the device can also optionally include a secondary working chamber supplied with pressurized fluid via a second rotating joint.
  • the intake circuit will be designed so as to make it possible to self-control the phase shift and, consequently, the vibratory power transmitted by the vibrator.
  • the vibrator comprises two trains 1, 2 of eccentric weights rotatably mounted by means of shafts A1, A2, An - A'1, A'2, A ' n parallel to a transverse axis X, X 'and the ends of which engage in bearings carried by two parallel flanges 3, 4 constituting the two lateral sides of a housing 5.
  • Each of the weights M, M ′ is associated with a pinion P arranged and dimensioned so that the pinions P associated with the same train 1, 2 of weights M mesh with each other, in successive pairs.
  • FIG 2 there are shown two sets of flywheels M each comprising a pair of sets of flywheels M / pinion P shown in solid lines, the assembly shown partially in broken lines indicating the mode of implantation of another couple.
  • the two flywheel trains are driven in rotation by means of a motorization, comprising two hydraulic motors H1, H2 mounted on the flange 3 at one end of the housing 5.
  • the pinions P2 and P4 are arranged so as to mesh with each other so as to ensure a rigid coupling (without sliding) between the two motors H1, H2.
  • the pinion P1 meshes with the pinion P integral with the counterweight M to effect the rotation drive of the train 2.
  • the pinion P3 is arranged so as to come to mesh with a pinion P5 integral with the driven shaft 6 of a phase shifter 7 with hydraulic control of the type shown in FIG. 4.
  • This phase shifter 7 furthermore comprises a driving shaft 8, coaxial with the driven shaft 6, which carries a pinion P6 engaged with the pinion integral with the counterweight M of the train 1.
  • the phase shifter 7 consists of a fixed structure 9, partly cylindrical, integral with the flanges 3, 4.
  • This structure is arranged so that the pinions P5, P6 and their main pivotings are contained in the housing 5 and that, on the other hand, the cylindrical part 10 of the structure housing the phase shifter 7, passes through the flange 3 and comes out on the outside, parallel to the motors H1, H2.
  • the tubular shaft 8 comprises a cylindrical inner surface successively having a smooth part 11 and a tapped part with helical teeth 12.
  • This cylindrical inner surface defines, with a cylindrical surface of the stepped shaft 6, an annular space 13 closed, on one side, by a ball bearing 14 ensuring the rotary and sealed mounting of one of the two shafts 6, 8 relative to the other and, on the other side, by a bottom 15 integral with the shaft 8 and through which the shaft 6 passes, with sealing.
  • the cylindrical surface of the shaft 6 successively comprises a smooth part 16 and a threaded part 17 with helical teeth.
  • the space E1 between the piston 20, the bottom 15 and the two shafts 6, 8, constitutes a first working chamber (main working chamber) into which a hydraulic fluid can be admitted thanks to an axial channel 25 produced in the 'tree 6.
  • This axial channel 25 opens into a rotary joint 26 provided at the end of the shaft 6 and the fixed part of which is integral with the structure 9.
  • This fixed part comprises a connection sleeve 27 to which the conduit of a hydraulic circuit.
  • the space E2 between the piston 20, the bearing 14 and the two shafts 6, 8, constitutes a second working chamber into which hydraulic fluid can be admitted by virtue of an axial channel 28 produced in the shaft 6 .
  • This channel opens into a rotating joint 29 provided at the end of the shaft 6 and the fixed part of which is integral with the structure 9.
  • this phase shifter is then as follows: In the absence of pressure inside the working chambers E1 and E2, the rotational driving torque of the train 1 of flyweights M causes a double phenomenon of screwing between the piston 20 and the shafts 6, 8. This screwing then causes an axial displacement of the piston 20 until it comes into end-of-travel abutment against the bottom 15.
  • this piston 20 When pressurized fluid is injected into the working chamber E1, this piston 20 is subjected to an axial force which tends to move it away from the bottom 15 and therefore to generate a double relative rotation between the two shafts 6, 8 and this, thanks to the combined action of the threads 17, 22 on the threads 12, 24.
  • the latter are designed so as to cause a relative double rotation of the shafts 6, 8 which can reach 180 ° (reshaping of the weights M).
  • An advantage of the previously described vibrator consists in that it makes it possible to overcome the transient phenomena which occur at start-up or when returning to stop.
  • a pressure is established in the working chamber E2 so as to bring the two mass trains -lottes in phase opposition, so that during this period, the vibrator generates practically no more vibrations.
  • the pressure is released in the chamber E2 so that the two trains 1, 2 of counterweights M can return to phase under the effect of the pressure established in the chamber E1 and, as a result, the vibrator generates vibrations along the working axis.
  • this object consists of a stake which one wishes to drive, as it is driven in, the power dissipated in the ground by friction increases and the resisting torque, by amplifying, ends up exceeding the couple transiting.
  • this self-control process makes it possible to reduce the risks of destruction or deterioration of objects subjected to vibrations. In addition, it avoids suffocating the heat engine used in the hydraulic power unit by requiring excessive power from the engine.
  • the secondary chamber E2 of the phase shifter can be connected to the hydraulic circuit supplying the motors H1, H2 (represented by the block CH in FIGS. 5 to 7), via a connection comprising a high pressure valve HP3 calibrated at the maximum admissible value of the hydraulic circuit supplying the motors.
  • a high pressure valve HP3 calibrated at the maximum admissible value of the hydraulic circuit supplying the motors.
  • the valve HP3 opens, so that the hydraulic fluid under pressure is injected into the secondary chamber E2 of the phase shifter.
  • This injection of fluid therefore causes the phase shifter to be actuated in the rephasing direction until the pressure of the hydraulic fluid in the circuit CH drops below the pressure HP3.
  • the motor H2 could be replaced by two motors having a total displacement equal to that of the motor H1.
  • Such an arrangement makes it possible, by supplying either one of the two motors, or both, to make a choice between the two operating modes priority power / priority moment.
  • the use of several hydraulic motors to drive the vibrator in rotation also has the advantage of making it possible to obtain a variation in the frequency of the vibrations, without having to use a hydraulic pump with variable flow.
  • This frequency variation can in fact be obtained by supplying only a determined number or all of the hydraulic motors, it being understood that the frequency obtained is imposed by the ratio between the flow rate of the hydraulic pump at constant flow rate and the sum of the engine displacement.
  • phase shifter 7 shown in FIG. 4 can be advantageously controlled using the hydraulic circuit shown in FIGS. 5 to 7.
  • phase shifter 7 has been shown schematically in the form of a double-acting cylinder comprising a main chamber E1 and a secondary chamber E2, this cylinder being returned to the rest position by a return spring which simulates resistance to driving.
  • the main chamber E1 is connected to the discharge chamber E3 of a second cylinder V, the working chamber E4 of which is connected to a first outlet S1 of a distributor D1.
  • the secondary chamber E2 of the phase shifter is, for its part, connected to the second outlet S2 of the distributor D1 and to a tank B by means of a valve calibrated at a relatively low pressure BP1 (here 20 b).
  • the two inputs I1, I2 of the distributor D1 are respectively connected to the tank B and to the output of a hydraulic pump 33 equipped with a constant flow regulator 34.
  • the first output S1 of this distributor D1 is also connected to the tarpaulin B, on the one hand, by via a first return circuit comprising a valve 35 calibrated at high pressure HP1 and, on the other hand, via a second return circuit comprising successively a distributor D2 and a valve 36 calibrated at high pressure HP2 (with HP2> HP1).
  • the phase shifter 7 is subjected to a pressure corresponding to the pressure HP1 (to the ratio of the surfaces of the pistons), this pressure serving to balance the resistant force exerted on the phase shifter 7.
  • the position of the piston 40 of the jack V is the image of the position of the piston 20 of the phase shifter 7, so that by locating the position of the rod of the jack V, the operator has the value of the phase shift generated by the phase shifter 7.
  • this phase shift value (and therefore the position of the piston 40) is not constant but is variable depending on the behavior of the object subjected to vibrations.
  • the chamber E4 of the jack V is subjected to the pressure of the fluid injected by the pump 33, which is established at the threshold value HP2 of the calibrated valve 36. Because it is greater than the pressure exerted in the chamber E3 (which corresponds to the resistant force which the phase shifter 7 undergoes), this pressure HP2 causes a displacement of the pistons 20 and 40 and, consequently, a rephasing of the phase shifter 7. When this rephasing reaches the desired value, the operator interrupts its action on the distributors D1, D2 and the circuit returns to the state previously described.
  • the safety of the vibrator is reinforced thanks to the fact that the chamber E2 of the phase shifter 7 is connected to the hydraulic circuit which supplies the motors H1, H2 thanks to a connection including a valve calibrated at high pressure HP3 and a limiter of debt. Thanks to this arrangement, any excessive pressure increase in the hydraulic circuit CH will cause a rephasing of the phase shifter 7 and a limitation of the amplitude of the vibrations.

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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)
  • Placing Or Removing Of Piles Or Sheet Piles, Or Accessories Thereof (AREA)
  • Combined Devices Of Dampers And Springs (AREA)

Claims (12)

  1. Schwingungserzeuger mit veränderlichem Moment, der zum Eintreiben von Gegenstanden in den Boden verwendbar ist, wobei dieser Schwingungserzeuger mindestens zwei exzentrische Fliehgewichtgänge (1, 2) verwendet, die je mindestens zwei exzentrische Fliehgewichte (M, M') aufweisen, welche drehbar auf fest mit zwei Ritzeln (P) verbundenen Wellen montiert sind, die so ineinandergreifen, daß sie mit Hilfe eines Motorantriebs in zueinander entgegengesetzte Richtungen drehen, der einen ersten Motor (H₁) und eine einen Phasenschieber (7) aufweisende Antriebsvorrichtung enthält,
    dadurch gekennzeichnet, daß der erste Motor (H₁) mit dem ersten Gang (2) von Fliehgewichten (M) über eine erste Ritzelanordnung (P₁) und mit dem zweiten Gang (1) über eine Antriebsvorrichtung (P₂ - P₆) gekoppelt ist, die sich von der ersten Ritzelanordnung (P₁) unterscheidet und den Phasenschieber (7) enthält, wobei dieser Phasenschieber (7) aufweist:
    - eine erste Antriebswelle (8), die drehbar auf einer in Bezug auf das Gehäuse des Schwingungserzeugers ortsfesten Struktur (4) montiert ist, wobei diese Drehwelle mindestens einen Abschnitt aufweist, der die Form einer zylindrischen Muffe hat, deren Innenbohrung eine erste Dichtfläche (11) gefolgt von einem ersten innengewindeten Abschnitt mit Schraubverzahnungen (12) aufweist,
    - eine zweite Antriebswelle (6) zylindrischer Form, die koaxial zur ersten Antriebswelle (8) drehbar angeordnet ist und die mit dieser einen ringförmigen Raum (13) abgrenzt, der auf einer Seite von einem Boden (15) verschlossen wird, wobei diese zweite Antriebswelle (6) aufeinanderfolgend eine zweite Dichtfläche (16) und einen ersten Außengewindebereich mit Schraubverzahnungen (17) aufweist,
    - ein ringförmiges Teil (20), das als in diesem ringförmigen Raum axial beweglicher Kolben dient und eine zylindrische Außenfläche, die aufeinanderfolgend eine dritte Dichtfläche (21), die dicht auf der ersten Dichtfläche (11) gleiten kann, und einen zweiten Außengewindebereich (22) enthält, der Schraubverzahnungen aufweist, die in die Zahnungen des ersten Innengewindeteils (12) eingreifen, und eine Innenfläche besitzt, die aufeinanderfolgend eine vierte Dichtfläche (23), die dicht auf der zweiten Dichtfläche (16) gleiten kann, und einen zweiten Innengewindeabschnitt (24) enthält, der Schraubverzahnungen aufweist, die in die Schraubverzahnungen des ersten Außengewindebereichs (17) eingreifen,
    - einen Einlaßkreis für unter Druck stehendes Fluid, der einen axialen Kanal (25) aufweist, der in der zweiten Antriebswelle ausgebildet ist und einerseits in der von den beiden Antriebswellen (6, 8) und dem ringförmigen Teil (20) abgegrenzten Arbeitskammer (E₁) und andererseits in einer Verteilungsleitung über eine Drehverbindung (26) mündet, die am Ende der zweiten Antriebswelle (6) montiert ist.
  2. Schwingungserzeuger nach Anspruch 1, dadurch gekennzeichnet, daß der Motorantrieb einen zweiten Motor (H₂) in Eingriff mit der Antriebsvorrichtung zwischen dem ersten Motor (H₁) und dem Phasenschieber (7) aufweist.
  3. Schwingungserzeuger nach Anspruch 1, dadurch gekennzeichnet, daß der Motorantrieb einen zweiten Motor (H₂) in Eingriff mit der Antriebsvorrichtung zwischen dem Phasenschieber (7) und dem zweiten Fliehgewichtgang aufweist.
  4. Schwingungserzeuger nach Anspruch 3, dadurch gekennzeichnet, daß die Motoren (H₁, H₂) Hydraulikmotoren mit gleichem Hubraum sind, um Schwingungen mit konstantem Moment zu erhalten.
  5. Schwingungserzeuger nach Anspruch 3, dadurch gekennzeichnet, daß die Motoren (H₁, H₂) Hydraulikmotoren sind und eine unterschiedliche Leistung entwickeln, um im Phasenschieber einen Druck proportional zur vollständigen absorbierten Leistung zu erhalten.
  6. Schwingungserzeuger nach Anspruch 3, dadurch gekennzeichnet, daß er einen dritten Hydraulikmotor in Eingriff mit dem zweiten aufweist, wobei diese beiden Motoren gemeinsam oder getrennt verwendbar sind und einen Gesamthubraum gleich dem des ersten Motors aufweisen, um entweder Schwingungen mit konstantem Moment oder Schwingungen mit konstanter Leistung zu erhalten.
  7. Schwingungserzeuger nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Motoren (H₁, H₂) und der Phasenschieber (7) auf der gleichen Seite des Schwingungserzeugers montiert sind.
  8. Schwingungserzeuger nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß das ringförmige Teil zwischen den beiden Antriebswellen (6, 8) eine sekundäre Arbeitskammer (E₂) abgrenzt, die an einen Einlaßkreis für Hydraulikfluid über einen zweiten axialen Kanal (28), der in der zweiten Antriebswelle ausgebildet ist, und über eine zweite Drehverbindung (29) angeschlossen ist, die sich entgegengesetzt der ersten befindet.
  9. Schwingungserzeuger nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Hauptkammer (E₁) des Phasenschiebers mit der Staukammer eines Arbeitszylinders (V) verbunden ist, dessen Arbeitskammer (E₄) an einen ersten Ausgang (S₁) eines Verteilers (D₁) über eine erste Rückleitung angeschlossen ist, wobei die Position des Arbeitszylinders (V) den Phasenverschiebungszustand des Schwingungserzeugers markiert.
  10. Schwingungserzeuger nach Anspruch 9, dadurch gekennzeichnet, daß die erste Rückleitung ein Ventil (35) aufweist, das auf einen hohen Druck (HP₁) austariert ist, daß die Arbeitskammer des Arbeitszylinders (V) außerdem an den Sammelbehälter (B) über eine zweite Rückleitung angeschlossen ist, die nacheinander einen Verteiler (D₂) und ein Ventil (36) aufweist, das auf einen Druck (HP₂) austariert ist, der höher ist als der Druck (HP₁), daß der erste Verteiler (D₁) zwei Eingänge (I₁, I₂) aufweist, die je mit dem Sammelbehälter (B) und einer Hydraulikpumpe (33) verbunden sind, und mindestens eine stabile Ruhestellung, in der er seine beiden Eingänge (I₁, I₂) miteinander in Verbindung setzt, während er seine beiden Ausgänge (S₁, S₂) verschließt, und eine erste umgeschaltete Stellung besitzt, in der er seinen ersten Ausgang (S₁) mit seinem zweiten Eingang (I₂) verbindet, und daß der zweite Verteiler (D₂) eine stabile Ruhestellung, in der er seinen Eingang (I₃) mit seinem Ausgang (S₃) in Verbindung setzt, und eine umgeschaltete Stellung aufweist, in der er seinen Eingang (I₃) von seinem Ausgang (S₃) isoliert.
  11. Schwingungserzeuger nach Anspruch 9, dadurch gekennzeichnet, daß der erste Verteiler (D₁) eine zweite umgeschaltete Stellung aufweist, in der er die Hydraulikpumpe mit der sekundären Kammer (E₂) des Phasenschiebers (7) in Verbindung setzt, während er die Arbeitskammer (E₄) des Arbeitszylinders (V) mit dem Sammelbehälter (B) in Verbindung setzt.
  12. Schwingungserzeuger nach einem der Ansprüche 8 bis 11, dadurch gekennzeichnet, daß die sekundäre Arbeitskammer (E₂) mit dem Hydraulikkreis (CH) verbunden ist, der die Motoren (H₁, H₂) mittels einer Verbindung speist, die ein auf einen hohen Druck (HP₃) austariertes Ventil einschließt, der einem Druck entspricht, der im Hydraulikkreis (CH) zulässig ist.
EP92401960A 1991-07-15 1992-07-08 Schwingungserreger mit einstellbarer Unwucht, insbesondere zum Eintreiben von Gegenständen in den Boden Expired - Lifetime EP0524056B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9109253A FR2679156B1 (fr) 1991-07-15 1991-07-15 Vibrateur a moment variable utilisable notamment a l'enfoncement d'objets dans le sol.
FR9109253 1991-07-15

Publications (2)

Publication Number Publication Date
EP0524056A1 EP0524056A1 (de) 1993-01-20
EP0524056B1 true EP0524056B1 (de) 1995-04-12

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EP92401960A Expired - Lifetime EP0524056B1 (de) 1991-07-15 1992-07-08 Schwingungserreger mit einstellbarer Unwucht, insbesondere zum Eintreiben von Gegenständen in den Boden

Country Status (7)

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US (1) US5253542A (de)
EP (1) EP0524056B1 (de)
JP (1) JP2769264B2 (de)
CA (1) CA2073518C (de)
DE (1) DE69202015T2 (de)
ES (1) ES2070604T3 (de)
FR (1) FR2679156B1 (de)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
NL1028140C2 (nl) 2005-01-28 2006-07-31 Dieseko Verhuur B V Trilinrichting.

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Publication number Priority date Publication date Assignee Title
FR2692523B1 (fr) * 1992-06-19 1994-10-07 Procedes Tech Construction Dispositif pour la commande d'un vibrateur à moment variable.
NL9401403A (nl) * 1994-08-31 1996-04-01 Dieseko Verhuur B V Overbrenging alsmede hiervan voorziene trilinrichting.
FR2735045B1 (fr) * 1995-06-09 1997-08-14 Pieces Beton Maintenance Distr Dispositif vibratoire, destine, notamment, a equiper des tables vibrantes utilisees, par exemple, dans la fabrication d'elements en beton
DE29614122U1 (de) * 1996-08-14 1996-09-26 Bauer Spezialtiefbau Gmbh, 86529 Schrobenhausen Schwingungserreger
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.
US5988297A (en) * 1998-03-24 1999-11-23 Hydraulic Power Systems, Inc. Variable eccentric vibratory hammer
NL1008965C2 (nl) * 1998-04-22 1999-10-25 Int Construction Equipment B V Werkwijze en inrichting voor het trillend aandrijven van een voorwerp.
US6504278B1 (en) 1998-05-08 2003-01-07 Gedib Ingenieurburo Und Innovationsberatung Gmbh Regulating device for adjusting the static moment resulting from unbalanced mass vibration generators
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EP0524056A1 (de) 1993-01-20
ES2070604T3 (es) 1995-06-01
FR2679156A1 (fr) 1993-01-22
DE69202015D1 (de) 1995-05-18
JPH05230833A (ja) 1993-09-07
JP2769264B2 (ja) 1998-06-25
FR2679156B1 (fr) 1993-10-29
CA2073518C (fr) 2003-01-14
US5253542A (en) 1993-10-19
DE69202015T2 (de) 1995-09-21
CA2073518A1 (fr) 1993-01-16

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