EP0153332B1 - Verfahren und vorrichtung zum vibrierenden betrieb eines arbeitskolbens, insbesondere für aktive arbeitswerkzeuge - Google Patents

Verfahren und vorrichtung zum vibrierenden betrieb eines arbeitskolbens, insbesondere für aktive arbeitswerkzeuge Download PDF

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Publication number
EP0153332B1
EP0153332B1 EP84902804A EP84902804A EP0153332B1 EP 0153332 B1 EP0153332 B1 EP 0153332B1 EP 84902804 A EP84902804 A EP 84902804A EP 84902804 A EP84902804 A EP 84902804A EP 0153332 B1 EP0153332 B1 EP 0153332B1
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EP
European Patent Office
Prior art keywords
piston
cylinder
control device
pressure fluid
pressure medium
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
EP84902804A
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German (de)
English (en)
French (fr)
Other versions
EP0153332A1 (de
Inventor
Achim Graul
Elmar Niedermeier
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Individual
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Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to AT84902804T priority Critical patent/ATE31641T1/de
Publication of EP0153332A1 publication Critical patent/EP0153332A1/de
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Publication of EP0153332B1 publication Critical patent/EP0153332B1/de
Expired legal-status Critical Current

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2203—Arrangements for controlling the attitude of actuators, e.g. speed, floating function
    • E02F9/221—Arrangements for controlling the attitude of actuators, e.g. speed, floating function for generating actuator vibration
    • 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
    • B06B1/183—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid operating with reciprocating masses
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/06—Means for driving the impulse member
    • B25D9/12—Means for driving the impulse member comprising a built-in liquid motor, i.e. the tool being driven by hydraulic pressure
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/36—Component parts
    • E02F3/40—Dippers; Buckets ; Grab devices, e.g. manufacturing processes for buckets, form, geometry or material of buckets
    • E02F3/402—Dippers; Buckets ; Grab devices, e.g. manufacturing processes for buckets, form, geometry or material of buckets with means for facilitating the loading thereof, e.g. conveyors
    • E02F3/405—Dippers; Buckets ; Grab devices, e.g. manufacturing processes for buckets, form, geometry or material of buckets with means for facilitating the loading thereof, e.g. conveyors using vibrating means
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21D—SHAFTS; TUNNELS; GALLERIES; LARGE UNDERGROUND CHAMBERS
    • E21D9/00—Tunnels or galleries, with or without linings; Methods or apparatus for making thereof; Layout of tunnels or galleries
    • E21D9/01—Methods or apparatus for enlarging or restoring the cross-section of tunnels, e.g. by restoring the floor to its original level
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/12—Fluid oscillators or pulse generators
    • F15B21/125—Fluid oscillators or pulse generators by means of a rotating valve

Definitions

  • the invention relates to a method according to the preamble of claim 1 and a device according to the preamble of claim 2.
  • Such pulse-hydraulic methods and devices are used in particular for operating the working tools of earthmoving equipment, such as total power controlled excavators, bulldozers, loaders etc. are used. Due to the vibrating movement of the tools, they are relatively easy to penetrate into hard-to-work soil classes. Smaller machines than previously can be used, particularly in the case of chemically consolidated sands and gravels, in hard coal and lignite, in coral, chalk, banked limestone, and in heterogeneous or weathered hard rocks, since their working efficiency is significantly improved by the pulse hydraulics.
  • a hydraulic vibration exciter is known from DE-A-2 623 639 and JP-A-54/149 083, which consists of a piston-cylinder unit acted on on both sides, a separate liquid supply line and a liquid discharge line being arranged on each side of the piston are. These lines can be opened or closed alternately via a control device, and a rotary slide valve can also be used as the control device. With the separate line routing for supply and return of the pressure medium, a constant exchange of the pressure fluid in the cylinder and in the lines is effected.
  • a rotary valve controlled piston cylinder device for causing axial piston vibration is also known from DE-A-2 821 339.
  • the rotary valve is integrated directly into the working piston and rotates around the piston feed axis.
  • the working piston itself is acted on on both sides and moves relative to the fixed rotary valve, so that pressure medium is alternately applied to the front or the rear of the piston via corresponding bores in the working piston.
  • a disadvantage of known devices is that high pressure peaks occur when the pressure medium return is closed by the control device. Under certain circumstances, these pressure peaks can be a multiple of the feed pressure and lead to damage to the hydraulic system or possibly also to the working tool.
  • Another object of the invention is to provide a pulse hydraulic device in an optimal manner in an earth moving device, e.g. in an excavator. In terms of the method, this object is achieved with a method which has the features in the characterizing part of patent claim 1.
  • the resetting of the piston by the reaction forces on the tool enables a particularly simple construction of the cylinder.
  • the reaction forces depend on constantly changing external conditions. So z. B. at the moment of overcoming resistance in the clod-like breaking of rock, the tensile strength practically collapses to zero. With the method according to the invention, no harmful pressure peaks can occur in such a state.
  • the working piston immediately moves to its maximum piston stroke and only oscillates slightly in the area of the relief opening.
  • the digging force of the excavator bucket is optimally used regardless of whether the excavator bucket is moved by hydraulic movement of the excavator arm or by driving the excavator forward.
  • the tasks are solved with a device having the features in the characterizing part of claim 2.
  • the pressure medium is circulated in the working chamber of the cylinder via the supply line and the return line. Since reaction forces are used on the working tool to reset the piston, the restoring force cannot always be controlled.
  • the maximum working stroke of the piston must therefore be limited so that no harmful pressure peaks or impacts can act on the piston. This is achieved in a particularly simple manner through the relief opening on the cylinder. As soon as this opening is uncovered when the maximum piston stroke is reached, pressure medium can flow out of the cylinder bypassing the control unit, so that no more thrust is exerted on the piston.
  • the feed line and the return line between control unit and cylinder are connected to one another in a manner that communicates with one another independently of the piston position via the cylinder.
  • the pressure medium volume in the lines can be used as a hydraulic damper as soon as the control unit blocks the return line.
  • the pressure medium is compressed by the restoring force, so that one suddenly setting pressure peak in the system is avoided.
  • the compressed pressure medium serves as a piston accelerator for reversing the piston movement as soon as the control unit releases the flow line.
  • the performance of the device can be further optimized if the return line is throttled to build up pressure in the cylinder. In this way, regardless of the constantly changing external conditions such as e.g. Pressure medium quantity, pressure medium temperature, restoring force, etc., build up a feed pressure that causes the piston to move.
  • the piston can be struck against a mechanical damping device in both end positions. With large restoring forces on the piston, it is thus mechanically and hydraulically damped. At the same time, the mechanical damping device also supports the acceleration of the piston against the restoring force. On the other hand, the piston is also damped in the opposite direction if, for example, the restoring force is suddenly interrupted by the release of the work tool and the piston is exclusively exposed to the hydraulic pressure.
  • the relief opening in the cylinder can only be exposed against the resistance of the damping device, it is achieved in a particularly simple manner that the piston vibrates even when its maximum piston stroke is reached. As soon as the piston opens the relief opening, pressure is reduced in the cylinder even when the return line is closed, so that even if there is no restoring force, the piston is reset by the damping device, so that the relief opening is closed again. As soon as the control device releases the flow line, the damping device is compressed again or the relief opening is exposed, so that the process is repeated.
  • a particularly advantageous construction of the damping device can be achieved if it consists of two disks loosely mounted on a piston section with a reduced diameter, between which a spring element is arranged, the axial movement of each disk being arranged by a stop arranged in the cylinder on the side facing away from the spring element is limited.
  • the damping takes place in both directions by the same spring element.
  • the damping path is the same in both directions.
  • the damping path between the two disks can be limited by at least one spacer.
  • An advantageous use of a device described above for an excavator bucket with vibrating teeth is characterized according to the invention in that the hydraulic cylinder is flanged directly to the control device and that the unit consisting of hydraulic cylinder and control device is arranged in a raised floor below the bucket.
  • the direct assembly of the control unit and hydraulic cylinder means that unnecessary pipes are no longer required and the pressure pulses can be transmitted to the piston in the cylinder with practically no pressure loss.
  • By placing the hydraulic unit directly on the work tool complicated and fault-prone mechanical power transmission elements such as e.g. Rods etc. away. Due to this arrangement, the excavator bucket itself contains a larger mass, which also only has a positive effect in work.
  • the excavator bucket works particularly advantageously if it is provided with an approximately U-shaped mouth, the legs of which are articulated at their free ends in the upper region of the bucket, if the connecting piece between the legs forms the bucket edge on the front and supports the teeth and if the connector is in turn articulated to the piston. Since the teeth to be moved are all attached to the U-shaped mouth, a complicated individual guidance of the teeth is avoided. Due to the articulation of the legs in the upper area of the spoon, the teeth do not move in a straight line, but move on a circular path section. However, this only has a positive effect in work, since it moves the excavated soil against the spoon bowl.
  • Disruptive transverse forces on the piston can be eliminated if the connecting piece is connected to the piston via a joint piece with two ball joints, one bearing shell of which is attached to the piston and the other of which is attached to the connecting piece.
  • a particularly simple construction results if several units consisting of hydraulic cylinder and control device are arranged in a row under the tray bottom and if the control devices can be activated with a common control shaft. All control units carry out exactly the same control movement via the common control shaft, so that the cylinders vibrate at the same time at a uniform frequency.
  • a working piston 15 moves in a hydraulic cylinder 1.
  • the hydraulic cylinder is connected to a control unit 2 via a feed line 9 and via a return line 10 bound.
  • the cylinder is supplied with pressure medium by means of the pump 4 from a pressure medium tank 3 via the suction line 5 and pressure line 7, the continuation of which, according to the control unit 2, is the flow line 9.
  • a pressure compensation store 5 is connected to the pressure line 7 via a further pressure line 8.
  • the conversion of the hydrostatic into a pulsating pressure medium flow takes place.
  • the control device alternately closes or opens the flow line 9 and the return line 10.
  • a hydraulic impact force P H thus acts on the end face 14 of the working piston 15.
  • the connection is blocked from B to T.
  • the impact force PH thus causes the piston 15 to move against the restoring force R, which is a reaction force on the working tool.
  • the control device blocks the flow line, ie interrupts the connection from P to A and then immediately opens the connection in the control device from B to T, the restoring force R, if present, begins to reset the piston 15 again.
  • the pressure medium flows via the return line 10 and the control unit 2 through the tank line 12 back into the pressure medium tank 3.
  • the movement which the piston 15 executes in the cylinder 1 depends on the restoring force R. If there is no restoring force R, the piston 15 is moved over the entire piston stroke S by the hydraulic impact forces P H. In this position, the piston 15 first strikes a mechanical damping device 18. If the piston 15 is moved further by the path X ′ against the force of the damping device 18, the piston 15 opens a relief opening 17, which is arranged as an annular groove in the cylinder 1. Via this relief opening, pressure medium can flow back through the relief line 11, bypassing the control unit 2, directly into the tank line 12. This results in a pressure reduction in the cylinder 1, regardless of the control position of the control unit 2, so that the piston 15 is moved back again without a restoring force R by the force of the damping device 18.
  • the relief opening 17 is closed again so that a hydraulic impact force P H can act on the piston again as soon as the control unit 2 releases the flow line 9. Obviously, a vibrating movement of the piston is achieved even if there is no restoring force at all, or if this is permanently less than the hydraulic impact force P H. At the same time, the maximum piston travel is limited by hydraulic measures by this arrangement, sudden loads being avoided by the damping device 18.
  • a throttle 24 in the return line between cylinder 1 and pressure medium tank 3 causes pressure to build up in cylinder 1 even when the connection from B to T is open in control unit 2, so that abrupt resetting of piston 15 at high restoring forces R is avoided.
  • Fig. 2 shows the pressure medium flow in the system at the start of a work process, i.e. with the piston 15 reset.
  • the control unit 2 is flanged directly to one end of the hydraulic cylinder 1.
  • the control unit 2 works according to the rotary slide valve principle known per se.
  • a drive device driven by a drive device, not shown, rotates a rotor 29 at a specific speed, which determines the frequency of the hydraulic pulses.
  • Flow pockets 28 and return pockets 26 are arranged in the rotor 29, which, depending on their positions, open or close inlet bores 27 and outlet bores 25 in the housing of control unit 2. 2, the flow pockets 28 expose the inlet bores 27, while the rotor 29 closes the outlet bores 25, since the return pockets 26 are in this position approximately transverse to the axis of the outlet bores 25.
  • the connection P to A is released, so that the end face 14 of the piston 15 is acted upon by pressure medium.
  • another control unit could also be used instead of the rotary slide valve principle.
  • the control device could have a control slide, which does not rotate, but executes an exclusively axial movement.
  • the piston itself consists of an actual working piston 15 and a guide piston 23. Between the working piston 15 and the guide piston 23 there is a section 30 with a reduced piston diameter. Two disks 21 are axially displaceably mounted on this section 30. A spring element 20 is arranged between the two disks 21 and presses the two disks 21 apart. Each disc 21 has a stop in the cylinder 1 on the side facing away from the spring element 20, against which it is pressed by the spring element 20. The disks 21 and the spring element 20 thus form in the simplest manner a mechanical damping device 18, against which either the working piston ring surface 19 or the guide piston ring surface 22 can be struck. Spacer elements are provided to protect the spring element 20 and to limit the damping path X. These spacer elements preferably consist of an annular wall arranged on each disk, so that each disk has the configuration of a cup disk. Of course, other spacing elements are also conceivable.
  • the hydraulic cylinder 1 is provided with an annular groove 16 on its side facing the control unit 2.
  • This annular groove 16 is connected via the return line 10 to the outlet bores 25 in the control unit.
  • the annular groove 16 is arranged such that there is a communicating connection between the feed line 9 and the return line 10 even when the piston 15 is completely reset. On the ring groove 16 can also be dispensed with if it is not necessary for reasons of enlarging the damping chamber 13.
  • the outlet bores 25 have a reduced diameter compared to the inlet bores 27, so that they act as a throttle in the pressure medium flow.
  • FIG. 4 A particularly advantageous use of the pulse hydraulics described in an excavator bucket is shown in FIG. 4.
  • An excavator bucket 32 is attached to a stick joint 42 on a dipper stick 31.
  • An approximately U-shaped mouth 33 is arranged in front of the spoon 32 and has two lateral legs 34. These legs 34 are articulated at their upper free end with jaw joints 35 in the upper region of the spoon. On their underside, the two legs 34 are connected to one another with a connecting piece 36, which on the one hand forms the spoon cutting edge 37 and on the other hand carries the teeth 38.
  • the bucket 32 has a raised floor consisting of an upper sheet 39 and a lower sheet 40. Control device 2 and hydraulic cylinder 1 are accommodated in this raised floor, each forming a unit. Depending on the width of the excavator bucket, several such units can be arranged in a row one behind the other.
  • the power transmission from the piston 15 to the connecting piece 36 of the jaw 33 takes place via a joint piece 41.
  • This joint piece has two ball joints 47, a bearing shell 48 being arranged on the piston 15 and a second bearing shell 48 'on the connecting piece 36.
  • This articulated connection also ensures that the vibratory forces are correctly transmitted from the piston 15 to the mouth 33 when the latter is tilted or displaced under tensile forces and resistance to penetration. Therefore, no special measures have to be taken to stabilize the piston 15.
  • the teeth 38 on the mouth 33 do not perform an exactly linear movement. Rather, the teeth 38 move about the axis of the jaw joint 35.
  • An upper cover plate 49 and a lower cover plate 59 on the connecting piece 36 ensure a perfect transition of the material lifted from the cutting edge 37 into the interior of the spoon 32.
  • the unit consisting of control unit and hydraulic cylinder 1 is supported on an abutment 51 to the rear.
  • the spoon is not only connected to the arm 31 at the arm joint 42, but also to the arm arm 44 and the toggle lever 45 at the arm joint 43 becomes.
  • the ladle Steering 43 is mounted in a metal-rubber element, since reaction forces attack here from the vibration of the mouth. Forces and reaction forces exerted by bucket cylinder 46 are transmitted simultaneously via spoon joint 43 here. It has proven to be particularly advantageous if the lever arm 44 in the basic position of the spoon 32 extends essentially parallel to the dipper stick 31.
  • Fig. 5 shows a modified embodiment of a control device, in which in particular the cylinder 1 and the piston 15 have a different design.
  • the piston is provided with a central bore 53 which leads from the end face 14 to the level of a piston ring groove 55.
  • the piston ring groove and the central bore are connected to one another via connecting bores 54 running transversely to one another.
  • a pressure relief and thus a limitation of the maximum piston stroke takes place as soon as the piston ring groove 55 reaches the relief opening 17.
  • the backflow of the pressure medium then also takes place via the relief line 11. This solution allows the relief opening 17 to be moved back, which can be advantageous with regard to the overall length of the piston.
  • the reset piston closes the return line 10 or the annular groove 16.
  • the front of the piston is provided with a conical bevel 56 which prevents the return line from suddenly closing.
  • this version can also be provided with a damping device.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • General Engineering & Computer Science (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Analytical Chemistry (AREA)
  • Chemical & Material Sciences (AREA)
  • Environmental & Geological Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Geology (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Actuator (AREA)
  • Operation Control Of Excavators (AREA)
EP84902804A 1983-08-06 1984-07-21 Verfahren und vorrichtung zum vibrierenden betrieb eines arbeitskolbens, insbesondere für aktive arbeitswerkzeuge Expired EP0153332B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84902804T ATE31641T1 (de) 1983-08-06 1984-07-21 Verfahren und vorrichtung zum vibrierenden betrieb eines arbeitskolbens, insbesondere fuer aktive arbeitswerkzeuge.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3328426A DE3328426A1 (de) 1983-08-06 1983-08-06 Arbeitswerkzeug fuer erdbwegungsgeraete
DE3328426 1983-08-06

Publications (2)

Publication Number Publication Date
EP0153332A1 EP0153332A1 (de) 1985-09-04
EP0153332B1 true EP0153332B1 (de) 1988-01-07

Family

ID=6205945

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84902804A Expired EP0153332B1 (de) 1983-08-06 1984-07-21 Verfahren und vorrichtung zum vibrierenden betrieb eines arbeitskolbens, insbesondere für aktive arbeitswerkzeuge

Country Status (10)

Country Link
US (1) US4715265A (fi)
EP (1) EP0153332B1 (fi)
JP (1) JPH0630845B2 (fi)
AU (1) AU565964B2 (fi)
CA (1) CA1237635A (fi)
DE (2) DE3328426A1 (fi)
FI (1) FI87150C (fi)
IT (1) IT1177930B (fi)
WO (1) WO1985000762A1 (fi)
ZA (1) ZA846016B (fi)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4825960A (en) * 1988-06-30 1989-05-02 Molex Incorporated Synchronized hydraulic hammer arrangement
US4959915A (en) * 1989-03-06 1990-10-02 Caterpillar Inc. Impact bucket apparatus
US5064005A (en) * 1990-04-30 1991-11-12 Caterpillar Inc. Impact hammer and control arrangement therefor
EP0927285B1 (en) * 1996-09-18 2001-03-14 Odin Ireland Excavation bucket incorporating an impact actuator assembly
JP3724758B2 (ja) * 1996-12-05 2005-12-07 株式会社小松製作所 切換バルブ装置
US6763661B2 (en) * 2002-05-07 2004-07-20 Husco International, Inc. Apparatus and method for providing vibration to an appendage of a work vehicle

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2426409A (en) * 1944-03-31 1947-08-26 Chicago Pneumatic Tool Co Distributing valve for percussive tools
US2699756A (en) * 1950-09-15 1955-01-18 Leonidas C Miller Reciprocating pneumatic actuator for tools
US3145488A (en) * 1962-12-26 1964-08-25 Deere & Co Vibrating bucket
DE1634824A1 (de) * 1967-03-11 1971-02-25 Haynes Louis Eduard Vorrichtung zum Ausheben eines Strassenkoffers bzw.zum Ausstechen einer Unterbausohle,eines Planums od.dgl.und zum Graben in der Erde
SE322469B (fi) * 1968-06-06 1970-04-06 Ilsbo Ind Ab
DE2008059A1 (de) * 1969-09-04 1971-09-09 Gunther Neumann Hydraulischer pneumatischer und mechaniser Antrieb für oszillierende Bewegungen
SE425468B (sv) * 1974-11-22 1982-10-04 Ts Osrodek P K Maszyn Gorniczy Hydraulisk slagmaskin
DE2607190C3 (de) * 1976-02-23 1981-07-16 Koehring Gmbh - Bomag Division, 5407 Boppard Hydraulischer Schwingungserreger für Vibrationsverdichter
DE2623639A1 (de) * 1976-05-26 1977-12-08 Kloeckner Humboldt Deutz Ag Hydraulischer schwingungserreger
DE2821339C3 (de) * 1977-05-18 1982-03-04 Kabushiki Kaisha Takahashi Engineering, Tokyo Hydraulische Kolbenzylindervorrichtung zum Erzeugen einer axialen Kolbenschwingung
FR2554179B1 (fr) * 1983-11-02 1986-01-03 Gtm Ets Sa Procede pour alimenter en fluide hydraulique, en continu et par impulsion controlee, un verin hydraulique travaillant normalement en continu, et dispositif pour la mise en oeuvre du procede

Also Published As

Publication number Publication date
DE3468339D1 (en) 1988-02-11
IT8448624A0 (it) 1984-07-24
FI87150B (fi) 1992-08-31
JPH0630845B2 (ja) 1994-04-27
US4715265A (en) 1987-12-29
IT1177930B (it) 1987-08-26
FI851392L (fi) 1985-04-04
CA1237635A (en) 1988-06-07
FI87150C (fi) 1992-12-10
EP0153332A1 (de) 1985-09-04
AU3157884A (en) 1985-03-12
DE3328426A1 (de) 1985-02-21
JPS60501959A (ja) 1985-11-14
FI851392A0 (fi) 1985-04-04
WO1985000762A1 (en) 1985-02-28
ZA846016B (en) 1985-04-24
AU565964B2 (en) 1987-10-01

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