EP0116164B1 - Appareil de battage par vibration - Google Patents

Appareil de battage par vibration Download PDF

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Publication number
EP0116164B1
EP0116164B1 EP83112971A EP83112971A EP0116164B1 EP 0116164 B1 EP0116164 B1 EP 0116164B1 EP 83112971 A EP83112971 A EP 83112971A EP 83112971 A EP83112971 A EP 83112971A EP 0116164 B1 EP0116164 B1 EP 0116164B1
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EP
European Patent Office
Prior art keywords
vibration
shafts
unbalance
motors
ram
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.)
Expired
Application number
EP83112971A
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German (de)
English (en)
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EP0116164A1 (fr
Inventor
Josef-Gerhard Tünkers
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Individual
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Individual
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Publication date
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Application filed by Individual filed Critical Individual
Priority to AT83112971T priority Critical patent/ATE31950T1/de
Publication of EP0116164A1 publication Critical patent/EP0116164A1/fr
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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
    • 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 ram with vibration damper and with two spaced and parallel to each other, a rigid vibration cell associated unbalanced shafts, each of the unbalanced shafts each having a special hydraulic motor and each unbalanced shaft assigned to at least one unbalanced mass and the motors the unbalanced masses in accordance with the angle of rotation with opposite directions of rotation drive so that the unbalance masses are substantially free of vibrations horizontally, in the vertical direction to generate a directional force without the need for a positive coupling between the unbalance shafts, their speeds can be synchronized, and the unbalance shafts are mounted in a plane perpendicular to the ramming direction, with the motors on the same source of hydraulic fluid is connected.
  • the current state of the art of these hydraulically operated vibratory rams represents a positively synchronized vibration cell with vibrations directed in the ram or pulling direction, on the upper part of which there is an elastically designed pulling head and on the lower part a clamping device firmly connected to the vibrator cell.
  • the unbalanced masses which are positively synchronized by means of gear drives, generate vibrations, the dynamic effect of which depends, among other things, on the static moment of the unbalanced masses and their operating speed.
  • the pulling head connected to the upper part of the vibrator cell has the task of isolating the vibrations to the load suspension device and thus to the carrier device, in particular to a crane, during pulling or ramming and to increase the ramming effect with its weight as a static load during ramming.
  • the relatively heavy load mass of the draw head is also suitable as a leader guide.
  • the clamping device connected to the lower part of the vibrator cell is used for the non-positive connection of the vibrating hammer to the pile.
  • the gearwheels used for the forced synchronization of the unbalance masses have a peripheral speed which is much too high, due to the dynamically required operating speed of the unbalance masses and the constructively required gearwheel diameter. It must be taken into account that the recommended circumferential speed of technically high-quality gearwheels is approximately v ⁇ 18 m / sec, while the circumferential speed actually occurring in such hydraulically operated vibratory rams is approximately 30 m / sec. This means that the gears in the forced synchronization couplings currently used are stressed to the limit of their load capacity.
  • the hydraulic pulling head has also had a disadvantageous effect on all hydraulically operated vibrating rams that have become known to date.
  • the relatively large dead weight leads to a constructionally high center of gravity of the vibratory hammer, with the result that, particularly when ramming, the top-heavy machine tilts or swings around the clamping parts on the pile and thus damages the pile. This also significantly increases the frequency of accidents.
  • the pulling performance is greatly reduced by the elastic pulling head. Due to the requirement, the vibrations against the carrier, so z. B. isolate against the crane, it is finally necessary to choose large in the vibrations occurring in practice (amplitude, frequency, acceleration), the load mass because of the "static self-suspension", which in turn adversely affects the above Balance hike affects the upper part of the elastic pulling head.
  • the spring elements dimensioned for this purpose in particular steel spiral springs and rubber thrust springs, can on the other hand only be used to a limited extent for the static preload when pulling. Therefore, overuse is the order of the day.
  • a vibratory hammer according to the preamble of claim 1 is previously known from DE-OS 21 35 393.
  • the housings of two identical three-phase electric squirrel-cage motors are rigidly connected to one another with the interposition of a plate.
  • a bracket with the interposition of a damping spring is attached, which is used for hanging on a traction rope, in particular an excavator.
  • a pair of pliers is attached to the underside of the jaw, which creates a rigid connection with the ram body.
  • the force required is between 5 to 10 t with a total unbalance force of 5 t and an unbalance frequency of 25 Hz.
  • the unbalances synchronize themselves automatically after the motors have started so that an amplitude is generated in the line of action of the force without the two motor shafts are rotatably connected to each other by means of a gear.
  • a vibrating ram for ramming or pulling a ramming body in particular a pile, a pipe, a sheet pile or the like, is proposed, with a pair of the same drive motors, each having a steep, essentially identical torque characteristic, the drive shafts of which each Equal-sized unbalance are provided and revolve in opposite directions of rotation and the housing are rigidly connected to each other, with a clamping device which exerts a force perpendicular to the connecting plane of the two axes of the drive shafts, and with a connecting element for rigid connection to the ram body at least in the line of action the force, the first drive motor pair being assigned at least one additional drive motor pair with the same drive motors within the pair, the plane determined by its shaft axes parallel to the shaft axis plane of the first motor Paares lies and that is rigidly connected to it at least in the line of action of the force.
  • All drive motors should be of the same design. It is also proposed to arrange the motor pairs one behind the other in the direction of the line of action of the force. Between two pairs of motors arranged with parallel shafts, a joint that can be moved at least about an axis parallel to the shafts of the pairs of motors should be provided. It is also proposed to arrange the axes of the shafts of the first pair of motors at an angle, in particular at right angles, to the axes of the shafts of the second pair of motors. Furthermore, an embodiment is proposed in which the axes of the shafts of the motor pairs lie in a common plane.
  • the unbalanced shafts are each driven by a hydraulic motor, the volume or pressure of which is from the pump supplied hydraulic fluid can be changed in stages or alternatively by changing the angular position of a controlled lever.
  • the unbalanced shafts are synchronized to achieve a directional vibration by a gear train.
  • FR-PS 1567678 discloses a vibratory ram in which two horizontal unbalanced shafts are each driven by a hydraulic motor in such a way that the shafts rotate in opposite directions and the weight is arranged so that their center of gravity lies in the same vertical plane. Furthermore, a clutch is provided between the drive mechanism and the unbalanced masses in such a way that they are positively coupled and thus positively synchronized. Gearboxes or belt drives should be considered as couplings.
  • the invention has for its object to provide a vibratory hammer according to the generic term, which can be produced with relatively simple constructive means, builds compact and thus handy.
  • any mechanical forced synchronization that is e.g. B. on gears, timing belts or other chain gears, but also on electric drive motors with their large dimensions, can be dispensed with.
  • the unbalanced masses self-synchronize if their shafts are individually driven by a hydraulic motor with opposite rotational movement in a rigid or fixed housing.
  • the counter-acting centrifugal force components of the unbalanced masses cancel each other out, so that the vibration ram is relieved of vibration in the horizontal direction, while a directed force is generated in the desired vertical direction.
  • Each unbalanced shaft is driven directly by a hydraulic motor, preferably with the interposition of a torsionally flexible coupling.
  • the hydraulic motors are preferably supplied with pressure fluid by a suitable pump, without the interposition of flow dividers, so that the unbalance masses at different speeds of the unbalance shafts force the synchronization via the pressure fluid of the common delivery line, since the hydraulic motors are hydraulically coupled to one another. As a result, the unbalance masses are synchronized automatically.
  • the self-synchronization can, however, only be effective if there are no masses arranged resiliently in the horizontal plane on the vibrator cell, ie the actual housing in which the unbalanced shafts are mounted. Therefore, one can advantageously dispense with an elastic pulling head which is fixedly arranged on the upper part of the rigid vibrator cell and which is functionally necessary in the previously hydraulically operated vibrating rams.
  • a vibratory hammer according to the invention is also very low, so that it can be handled particularly well.
  • This also avoids the disadvantageous wandering of the center of gravity with the above-described disadvantageous properties.
  • the vibration-isolated pulling head can be arranged exactly in the vertical direction between the excitation cells, that is to say between the hydraulic motors. This results in an optimally low overall height of the entire vibrating ram, which results in an exact ramming guide, because the distance of the overall center of gravity, based on the ramming clamp point, is very small.
  • the vibration isolation between the load suspension device, in particular a crane hook, and the actual vibrator cell is achieved by at least one spring element interposed.
  • This vibration damper makes it possible that an optimal static preload is exerted on the hydraulically driven vibrating ram during pulling, without having to accept the disadvantages described in the known vibrating rams, such as. B. high center of gravity and low tensile strength of the spring elements.
  • a vibration damper as described in DE-OS 28 23 953 is particularly advantageous.
  • at least one spring element which is loaded transversely to the direction of pull, that is to say in the horizontal is loaded essentially under pressure between a flexible and / or flexible pulling element, in particular a rope, attached to the load suspension device, in particular to the crane hook, and a flexible pulling element attached to the vibrator cell.
  • the z. B. can consist of a barrel-shaped bulge formed from a rubber-elastic properties elastomer body, which is arranged between it on pressure-bearing abutments, which convert the vertical and tensile and dynamic loads in a substantially horizontally loading loads on the spring body.
  • a dimensionally stable endless loop made of rope, wire, tape or other material, or of four endless loops of rope, wire, tape or other material which are movably connected to one another, is provided with two support plates arranged opposite each other in the pulling direction, with between the support plates one or more damping bodies made of rubber or other material is arranged movably transversely to the pulling direction and occurs under load in the pulling direction Changes in distance between the support plates serve as compressive forces for changing the length of the damping body or the damping body and for changing the distance between the guide and fastening plates or the like, which are held transversely to the pulling direction.
  • An embodiment of such a vibration damper is characterized in that four endless loops of the same length and of the same strength, made of rope, wire, tape and other flexible or flexible material, are used to form the endless loop.
  • two opposite guide and mounting plates can be provided, which form the abutments. The distance between the two abutments is changed depending on the load.
  • Each support plate can be arranged held by two levers or loops and each abutment also held by two endless loops or levers such that the support plates are in the pulling direction and the abutments in the transverse direction are opposite.
  • Each of the four endless loops or levers can be connected to a support plate at one end and to an abutment at the other end.
  • the elastic pulling head also known as "load mass”
  • the elastic pulling head has the task of establishing the connection to the carrier device (crane) in order to guide the vibrating bear with ramming material during ramming and to support the vibrating bear with a corresponding static pulling force when pulling.
  • this task must be combined with the isolation of the vibration effect of the vibration exciter towards the crane.
  • rubber buffers loaded with thrust are used to isolate the vibration effect.
  • the size of the static pulling force which is required for pulling and must be transferred from the rubber buffers, is approximately 0.3 to 0.5 times the centrifugal force. The size of the rubber buffers is therefore determined by the static tensile force to be transmitted.
  • the elastic pulling head lies perfectly on the excitation cell during vibration - vibration-isolated.
  • this requirement is only met if the required static deflection of the mass M2 via the rubber buffers is ensured by a correspondingly large dead weight of the drawing head (mass M 2) at the vibration frequency (interference frequency) that occurs.
  • the deflections are known as empirical values for certain vibration frequencies.
  • this elastic pulling head (load mass) can be dispensed with entirely as part of the self-synchronizing drive.
  • the clamping pliers will not be described further here. As a mass firmly connected to the vibration exciter, it forms the vibrating mass M1 in the further considerations with the mass of the vibration exciter.
  • the elastic pulling head (load mass) with its weight mass M2 is completely dispensed with and the tensile force is articulated directly on the vibration exciter. All the disadvantages described above with the elastic pulling head are eliminated from the outset.
  • the hydraulic motors are particularly compact with large outputs.
  • the entire vibratory hammer can be built in a particularly compact manner.
  • the reference number 1 denotes a rigid housing, in particular made of steel, which forms the vibrator cell.
  • Two unbalanced shafts 2 and 3 are rotatably mounted in the housing 1 at a distance and parallel to one another.
  • Each unbalanced shaft 2 or 3 is assigned an individual hydraulic motor 4, 5, which can be regulated in particular in its speed, which drives the unbalanced shaft 2 or 3 in question, in the present case with the interposition of a torsionally flexible coupling 6 or 7.
  • At least one unbalanced mass 8 or 9 is arranged on each unbalanced shaft 2 or 3, which is driven by the respective unbalanced shaft 2 or 3. The arrangement is such that the unbalanced shafts 2, 3 are opposite each other, for. B.
  • the unbalanced shaft 2 in direction A and the unbalanced shaft 3 in direction B is driven by the associated hydraulic motor 4 or 5.
  • hydraulic motors 4, 5 z. B. hydrostatic motors are used. Even if a motor leaks or if hydraulic fluid is applied unevenly, the unbalanced masses will force the synchronization of your speeds. It is therefore not important to provide the hydraulic motors with the most accurate hydraulic fluid quantities per unit of time. Rather, it is even possible to use hydraulic motors 4, 5 only from a common suitable, in particular controllable, z. B. hydrostatic pump to drive, all hydraulic motors can be connected to a delivery line.
  • the unbalanced masses ensure, via the hydraulic pressure medium, that the unbalanced shafts 2 and 3 rotating in opposite directions of rotation always rotate at the same speed, the unbalanced masses 8 and 9 synchronizing dynamically.
  • the self-synchronization of the unbalanced masses 8 and 9 takes place through the horizontal centrifugal force components F H , which cancel each other out in the horizontal plane of the vibrator cell 1, so that the housing 1 is relieved of vibrations in the horizontal plane.
  • the components add up, so that the desired ramming or pulling effect is achieved.
  • a bearing 10 for. B. formed by a sheet metal tab, arranged, in particular welded, which has a bearing eye 11 with which a load-carrying means 12, for. B. a crane hook, but also a link element of a vibration damper, generally designated by the reference number 13 (FIG. 1), can be coupled in an articulated manner.
  • the load-carrying means 12 can also be a flexible tension element, e.g. B. a rope, which via a coupling 14, d. H. via a joint with which the vibration damper 13 is connected.
  • the reference numeral 15 is also a Designated traction element, which leads to a load suspension device, in particular to a crane hook, not shown.
  • the pulling element 15 can also be a rope which is connected via a coupling 16, e.g. B. also via a joint with the vibration damper 13 is coupled.
  • the reference numerals 17, 18, 19 and 20 denote handlebars, which are preferably flexible, z. B. also flexible traction elements, especially ropes.
  • 21, 22 and 23, 24 denotes couplings, for. B. joints on which the handlebars or tension elements are arranged. All couplings 16, 21, 22, 23 and 24 have in particular a degree of freedom and can be pivoted about at least one horizontal axis each. Of course, within the scope of the inventive concept (object and solution) there are also embodiments in which the couplings 16, 21, 22, 23, 24 are designed as spatial joints.
  • the joints 21, 22 and 23, 24 are assigned pressure abutments 25 and 26, which can consist of rigid steel plates.
  • a spring element 27 Arranged between the pressure abutments 25 and 26 is a spring element 27 which, in the present case (FIG. 1), has a barrel-shaped basic shape directed outwards and can be hollow, that is to say barrel-shaped, in its interior (not shown).
  • the spring element 27 consists of a resilient plastic material, in particular an elastomer. Suitable polyurethanes or polyamides are suitable. You will use plastics that have the required level of dimensional stability, rebound resilience, and resistance to the greases, oils and aggressive media commonly found on construction sites, as well as being lightfast.
  • a drawing head (Fig. 1) is referred to, which guides and holds the material 29 to be rammed or drawn in the usual manner.
  • the spring element 13 keeps all harmful vibrations away from the vibrating hammer 1 to the crane hook, not shown, since the vibrations occurring during ramming or pulling can be absorbed by the spring element 27 due to its pressure load.
  • the links 17, 19 around their articulation points 21, 23 horizontal vibrations cannot propagate via the tension element 15 onto the crane or the like.
  • the links 18 and 20 will swing more strongly around their bearings 22 and 24, respectively. The result is a housing 1 which is completely calm in the horizontal plane and the avoidance of the load suspension means jumping or hitting the crane.
  • This embodiment is suitable for the use of hydraulically driven vibratory rams on a leader 30.
  • a leader guide 31 is arranged on the vibrator cell 1 in such a way that the mass of this leader guide 31 is as stiff as possible in the horizontal plane, but on the vertical plane is resiliently vibration-isolating .
  • a metallic support body 32 is attached, in particular welded or screwed, to the top of the housing 1, which is encompassed by a U-shaped part, the U-legs 33 and 34 of which are spaced apart from the outer surfaces of the support body 32 run such that within this gap distance a rigid spring 35 or 36 is arranged, which is loaded in the horizontal plane to pressure and thus has a high rigidity, while the springs 35 and 36 are loaded in the vertical plane to thrust and Ensure high elasticity in this load level.
  • Both the leader 30 and the leader guide 31, the U-legs 34, 35 and the support body 32 consist of a rigid material, in particular steel.

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  • Engineering & Computer Science (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)
  • Placing Or Removing Of Piles Or Sheet Piles, Or Accessories Thereof (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)

Claims (3)

1. Sonnette vibratoire à atténuateur de vibrations (13) et à deux arbres déséquilibrés (2,3) montés parallèles sur palier et subordonnés à une cellule vibratoire rigide (1), un moteur hydraulique (4,5) étant affecté à chaque arbre déséquilibré (2,3), et une masselotte (8,9) au moins étant affectée à chaque arbre déséquilibré, les moteurs (4,5) entraînant les masselottes (8,9) conformément à l'angle de rotation, chacune dans un sens opposé à l'autre, de sorte que les masselottes (8,9) sont à vitesses synchronisables sur le plan horizontal pratiquement sans vibrations, et dans le sens vertical pour engendrer une force dirigée, avec renonciation à l'emploi d'un couplage forcé entre les arbres déséquilibrés (2,3), lesquels (2,3) sont en appui sur palier selon un plan perpendiculaire au sens de pilonnement de la sonnette, les moteurs (4,5) étant reliés à la même source de liquid de hydraulique sous pression, caractérisée en ce que l'on n'utilise que deux moteurs hydrauliques (4,5) raccordés à une conduite de refoulement reliée à la source de liquide hydraulique sous pression, de sorte que les moteurs hydrauliques (4,5) sont hydrauliquement couplés l'un à l'autre et que l'atténuateur de vibrations (13) ainsi que d'éventuelles masses de surcharge sont reliés par articulation à la cellule vibratoire (1).
2. Sonnette vibratoire selon revendication 1, caractérisée en ce que les moteurs hydrauliques (4,5) et/ou la pompe hydraulique affectée à ceux- ci est/sont conçu(e)(s) de sorte à pouvoir régler leur nombre de tours.
3. Sonnette vibratoire selon revendication 1 ou 2, caractérisée en ce que les moteurs hydrauliques (4,5) sont conçus comme des moteurs hydrostatiques.
EP83112971A 1983-02-03 1983-12-22 Appareil de battage par vibration Expired EP0116164B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT83112971T ATE31950T1 (de) 1983-02-03 1983-12-22 Vibrationsramme.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3303574A DE3303574C1 (de) 1983-02-03 1983-02-03 Vibrationsramme
DE3303574 1983-02-03

Publications (2)

Publication Number Publication Date
EP0116164A1 EP0116164A1 (fr) 1984-08-22
EP0116164B1 true EP0116164B1 (fr) 1988-01-13

Family

ID=6189893

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83112971A Expired EP0116164B1 (fr) 1983-02-03 1983-12-22 Appareil de battage par vibration

Country Status (5)

Country Link
US (1) US4625811A (fr)
EP (1) EP0116164B1 (fr)
JP (1) JPS59145828A (fr)
AT (1) ATE31950T1 (fr)
DE (1) DE3303574C1 (fr)

Families Citing this family (18)

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Publication number Priority date Publication date Assignee Title
ATE50815T1 (de) * 1985-12-13 1990-03-15 Plasser Bahnbaumasch Franz Einrichtung zum eintreiben von fundamentrohren od. dgl. in erdschichten mittels vibrationsvorrichtung.
US4819740A (en) * 1987-11-16 1989-04-11 Vulcan Iron Works Inc. Vibratory hammer/extractor
GB2226616A (en) * 1988-06-24 1990-07-04 Mbw Inc Improved vibratory mechanism for a compaction roller
US5088565A (en) * 1990-03-23 1992-02-18 J & M Hydraulic Systems, Inc. Vibratory pile driver
DE4139798C2 (de) * 1991-12-03 1995-08-17 Tuenkers Maschinenbau Gmbh Vibrationsbär
US6129159A (en) * 1998-12-24 2000-10-10 Mpi Drilling Vibratory drill head apparatus
US6966448B1 (en) * 2000-08-23 2005-11-22 Darryl Scott Burkett Trailer-mounted crane apparatus
US6896071B1 (en) * 2002-08-15 2005-05-24 John Edward Collins Drive systems and methods for sheet piles
US20040188118A1 (en) * 2003-03-26 2004-09-30 Mcphee Robert Vibratory post driving device
US7080958B1 (en) 2005-04-27 2006-07-25 International Construction Equipment, Inc. Vibratory pile driver/extractor with two-stage vibration/tension load suppressor
US7913771B2 (en) * 2007-12-21 2011-03-29 American Piledriving Equipment, Inc. Battery operated cordless vibratory pile driver
US7704017B2 (en) * 2008-04-30 2010-04-27 Pileco Inc. Friction shaft coupling with perpendicular adjustment
US8336643B2 (en) 2010-08-13 2012-12-25 Ronald Harleman Vibratory drilling apparatus
US10392871B2 (en) 2015-11-18 2019-08-27 American Piledriving Equipment, Inc. Earth boring systems and methods with integral debris removal
US9957684B2 (en) 2015-12-11 2018-05-01 American Piledriving Equipment, Inc. Systems and methods for installing pile structures in permafrost
NL2017953B1 (en) * 2015-12-14 2018-04-10 High Five Solutions B V Assembly and method for driving one or more sheet piles into or out of the ground.
EP3228392B1 (fr) * 2016-04-05 2019-08-28 BAUER Maschinen GmbH Appareil de battage à vibrations
DK3243573T3 (en) * 2016-05-09 2018-10-29 Eurodrill Gmbh Vibration Generator

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Publication number Priority date Publication date Assignee Title
US2420793A (en) * 1944-06-09 1947-05-20 John C O'connor Vibratory drilling apparatus
US3004389A (en) * 1959-04-25 1961-10-17 Muller Ludwig Device for varying the frequency of a vibration exciter
GB1114711A (en) * 1964-06-02 1968-05-22 John Carnegie Orkney Improvements in or relating to a method of inducing periodic stress and strain in an elongate elastic element
AT262012B (de) * 1965-03-22 1968-05-27 Venanzetti Vibrazioni S A Vibrationseinrichtung
US3312295A (en) * 1965-09-23 1967-04-04 Jr Albert G Bodine Method and apparatus for fluid injection in vibratory driving of piles and the like
BE715853A (fr) * 1967-06-02 1968-10-16
DE2135393A1 (de) * 1971-07-15 1973-02-01 Delmag Maschinenfabrik Ruettelvorrichtung zum einrammen oder ziehen eines rammkoerpers, insbesondere eines pfahles und dgl
US3828864A (en) * 1973-02-26 1974-08-13 H & M Vibro Inc Pile driver and extractor
JPS5185211A (ja) * 1975-01-22 1976-07-26 Minoru Kuroda Shindokuiuchikinokishinsochi
DE2600173A1 (de) * 1976-01-05 1977-07-14 Mueller & Co Masch Fernthal Baggermaeklereinrichtung zum rammen und ziehen von rammprofilen
US4135585A (en) * 1977-09-09 1979-01-23 Wagner Gary L Drill rig-casing driver assembly
DE2823953C2 (de) * 1978-06-01 1985-01-24 Tünkers Maschinenbau GmbH, 4030 Ratingen Aufhängevorrichtung für Rüttelbären an einem Lastaufnahmemittel
JPS5652224A (en) * 1979-10-05 1981-05-11 Nippei Toyama Corp Pile driver

Also Published As

Publication number Publication date
ATE31950T1 (de) 1988-01-15
DE3303574C1 (de) 1984-09-06
JPS59145828A (ja) 1984-08-21
EP0116164A1 (fr) 1984-08-22
US4625811A (en) 1986-12-02

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