US3916768A - Hydraulic cylinder for providing reciprocation of a hydraulic jack - Google Patents

Hydraulic cylinder for providing reciprocation of a hydraulic jack Download PDF

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Publication number
US3916768A
US3916768A US333555A US33355573A US3916768A US 3916768 A US3916768 A US 3916768A US 333555 A US333555 A US 333555A US 33355573 A US33355573 A US 33355573A US 3916768 A US3916768 A US 3916768A
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conduit
fluid
chamber
valve means
piston
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US333555A
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English (en)
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J Louis E Martin
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Poclain SA
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Poclain SA
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    • 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
    • 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

Definitions

  • This invention relates to a device for feeding a doubleacting jack.
  • a rotary engine is coupled to the jackfeeding distributor in order to place the chamber of this jack in communication either with the delivery of a pump or with -a fluid reservoir.
  • One application of this feed is the production of a vibration generator.
  • the subject invention is in the field of vibration generating equipment and is specifically directed to hydraulic fluid control circuitry associated with a fluid actuating jack comprising a hydraulic cylinder and piston assembly which is operated to provide cyclic reciprocation of the piston member and rod assembly with respect to the cylinder.
  • hydraulic jack assemblies for positioning of machine elements or the like is well-known and has been used for many years. Such usage is primarily for the purpose of positioning a member in a fixed position in which it remains for at least a short time period.
  • Other fluid actuated hydraulic jack members have been employed for providing vibration by the cyclic reciprocation of the piston in the hydraulic cylinder. Such devices have been of particular use in material fatigue testing operations.
  • a jack comprising a hydraulic cylinder and piston assembly with automatic reciprocation of the piston within the cylinder being effected by the inventive hydraulic control circuitry.
  • the piston is acted upon by a biassing force applied to the piston rod side of the cylinder tending to move the piston in a direction moving the rod into the confines of the cylinder.
  • the cyclic application of hydraulic fluid at a pressure sufficiently high to overcome the aforementioned biassing force is provided in the cylinder on the side of the piston opposite the piston rod so as to achieve a reciprocation of the piston under the control of the application of the pressurized hydraulic fluid.
  • the system includes:
  • a distributor valve spool member movable between two end positions first, second and third conduits connecting said distributor to the working chamber, fluid reservoir and source of pressurised fluid repsectively, whilst, in its first end position, the distributor places the first and third conduits in communication and blocks the second conduit; in its second end position, the distributor places the first and second conduits in communication and blocks the third conduit.
  • a calibrated valve is disposed on the fifth conduit between the fluid reservoir and the delivery of the rotary engine.
  • a sixth conduit connects the first conduit to the part of the fifth conduit between said rotary engine and calibrated valve, whilst a nonreturn valve is disposed on said sixth conduit, allowing the fluid to pass from the fifth conduit towards the first conduit.
  • a seventh conduit advantageously connects said first conduit to the source of pressurized fluid, whilst another nonreturn valve is disposed on said seventh conduit allowing the fluid to pass from the first conduit towards the source.
  • the seventh conduit is preferably connected to the source, by being connected to the part of the fourth conduit included between said source and the restriction.
  • the subject invention additionally includes an accumulator conduit connecting a pressurized fluid accumulator to the source of pressurized fluid comprising the output from a power driven pump.
  • a second distributor valve is disposed in the accumulator conduit for enabling communication of pressurized fluid in the accumulator with the source of pressurized fluid in a first position but being movable to a second position to block the accumulator conduit and prevent communication between the pressure accumulator and the source of pressurized fluid.
  • the restriction in the fourth conduit is an adjustable valve member which is adjustable for providing a desired flow rate to the rotary engine driving the distributor valve so as to enable adjustment of the frequency of reciprocation of the piston rod assembly.
  • the second conduit is connected to the fluid reservoir through a connection to the fifth conduit.
  • the distributor valving means can either be a reciprocating valve or a rotary valve member.
  • the jack is a single-action jack in that it only has one working chamber into which the pressurized hydraulic fluid is injected.
  • An elastic member such as a spring or the like is interposed in the cylinder on the side of the piston opposite the side in which pressurized fluid is provided to oppose the movement of the piston caused by the pressurized fluid so that a lowering of "the pressure in the working chamber below a preset level will permit the elastic element to move the piston to an extreme end position.
  • the jack is a double-acting jack.
  • a piston rod is coupled to the piston of this jack, this piston defining, inside the cylinder, a first chamber of larger volume having one portion defined by the face of the piston from which the piston rod does not extend and a second chamber of smaller volume having one portion defined by the face of the piston from which the piston rod extends.
  • the larger chamber constitutes the working chamber and the smaller chamber is connected by a ninth conduit to the source of pressurized fluid for moving or returning the piston to an end position when the source of pressurized fluid is not connected to the larger chamber.
  • the source of pressurised fluid with which the third conduit and the source of pressurised fluid with which the ninth conduit is connected are advantageously ment of the invention.
  • FIG. 8 is aschematic diagram of another embodi-j 3 comprise a single pump.
  • the variant is sometimes preferred in which the source of pressurised fluid with which the third conduit is connected is a pressurised fluid accumulator, whilst the sourceof pressurised fluid with which the ninth conduit is connected is a pump.
  • the jack is a double-acting jack
  • a piston rod is coupledto the piston of this jack and this piston defines, inside the cylinder, a large chamber and a small chamber, the piston rod being at least partly contained in said small cham-' her.
  • the small chamber in this embodiment constitutes v the working chamber, whilst the large chamber is connected to a source of pressurised fluid by a tenth conduit and the pressurised fluid that may be contained'in said large chamber constitutes the return device.
  • An elastic element is interposed between the cylinder and the piston and its effect is antagonistic to thatof fluid contained in the largechamber.
  • FIG.,1 is a schematic illustration of a preferredem- DRAWINGS bodiment of the invention
  • restriction 21 mounted in the conduit 19 serves to control theamount of fluid flowing through conduit 19.
  • the distributor 13 can assume a third orinterrnediate position which is not shown in the drawings but in which the conduit 14 is blocked.
  • a calibrated valve 22 is disposed'o'n the conduit 20.
  • Conduit 14 is connected to I the part of conduit included between the exhaust of i 'called by a conduit 23.
  • a so-called first nonretum valve the-rotary'engine 18 and the calibrated valve 22 so- 24 is mounted in conduit '23 and allows the fluid to pass 1 from conduit 20 towards conduit 14.
  • FIG. 2 is a simplified schematic diagram of the embodiment of FIG. 1 illustrating the distributor in an end position causing movement of the piston to the left;
  • FIG. 3 is a simplified schematic viewof the embodiment of FIG. 1 illustrating the distributor in its second end position in which the piston would move to the 7 right as illustrated therein;
  • FIG. 4 is a perspective view with parts removed of rotary distributor means operable in the FIGS. 1-3; I
  • FIG. 5 is a schematic illustration of another embodiment of the invention.
  • FIG. 6 is an enlarged sectional view of an adjustable" .FIG. 5;
  • FIG. 7. is a schematic diagram of another embodiment of the ,inventiomandv ment of the invention.
  • FIG. 1 shows a device which comprises a double-acting jack 1 provided with a piston 2 and a piston rod 3.
  • the chamber 4 inwhich the piston rod 3 is disposed, has a so-called small useful section, smallerthan the so-called large useful section, of the chamber 5 opposite thereto.
  • a body 6 is fixed to the rod 3 by means of a housing 7 with which it is provided and a pin 8 or like means.
  • the device further comprises a fluid reservoir 9 and a pump 10, the inlet of which is connected to the reser-
  • a conduit 25 connects conduit l4'to conduit 12.
  • a so-called second nonretum valve 26 is disposed on this conduit 25 and allows the fluid to pass from conduit 14 towards conduit 12.
  • FIG. 2 shows a simplified diagram of FIG. 1. It consists in connecting conduit 25 to conduit 12, not directly, but connecting said conduit 25 to the part of conduit 19 included between" conduit 12 and the restriction 21. Similarly; conduit 15 is connected to the fluid reservoir 9 by means of conduit 20, with which it embodiment of voir 9 by a conduit 11. A conduit 12 connects the delivample of which is shown in FIG. 4, with a rotary engine 18. The distributor 13 is connected by conduit 14 to is connected.
  • FIG. 4 shows a rotary type distributor 13 known per se. It is constituted by a cylindrical body 27, inside which a rotor 28 is mounted to rotate.
  • the rotor 28 is provided with hollowed out sectors 29, separated by solid sectors 30 and has a shaft 3l which is provided with a connecting flange 32.
  • the engine 18 also has a driven shaft 33 provided with flange 34, the flanges 32 and 34 being fixed together by bolts 35.
  • the conduits 14, 15, and 16 are in factdivided into two, viz. 14a, 14b, 15a, 15b, 16a, l6b,where they are connected with the rotary distributor 13. It is noted that the distributor 13 shown in FIG.
  • FIG. 4 operates to provide communication between the various conduits and blockage of the various conduits exactly as described with respect to FIG. 1'.
  • FIG. 4 is certainly advantageous, but is not the onlyone that may be chosen.
  • a rectilinearly moving slide distributor as in FIG. 1 coupled with a tierod-crank system or with an eccentric may fulfill the function devolving upon the rotary distributor 13.
  • FIG. 5 illustrates an embodiment of the inventionsimilar to FIG. 1 with the exception that the embodiment of FIG. 5 employs an adjustable flow restricting means 21a and also employs a pressurized fluid accumulator device 36.
  • a second distributor 38 which merely constitutes an on-off valve is mounted in an accumulator conduit-defined by conduit portions 37a and 371 as clearly shown in FIG. 5.
  • the second distributor 3 8 is movable between one or two positions with the first position being as illustrated in FIG. 5 in which the pressure accumulator is in communication with conduit 12.
  • the second positionof the distributor 38 is essentially a blockage position in which the pressure accumulator is isolated.
  • FIG. 6 shows an embodiment, known per se, of the adjustable restriction 21a.
  • the conduit 19 is provided with a boss 39 which restricts the section of passage thereof.
  • a piece 40 is mounted to slide on the conduit 19, in which it is introduced through an opening 41 with interpostion of gaskets 42..
  • the piece 40 is partly disposedopposite the section of passage 8 of the conduit 19, at thelevel of the boss 39, and restricts this section to a values lower than valu'e S.
  • a support 43 is welded to the conduit 19 and is provided with a threading complementary to that of a threaded screw 44 inserted therein.
  • the screw 44 isprovided with a wheel 45 for controlling its rotation.
  • One of the ends of the screw 44 is inserted into an aperture 46 with which the piece 40 is provided and is integral in translation with said piece 40 by means of two pairs of nuts-counternuts 47.
  • the device is the same as in FIG. 1, except that the jack 101 shown is a singleaction jack.
  • the piston 102 mounted to slide in the cylinder of the jack 101 thus defines with said cylinder :1 single working chamber 105.
  • the piston rod 103 is fixed to the piston 102 and is partly contained in chamber 104 opposite chamberl05.
  • a spring 106 is disposed in the chamber 104 between the piston 102 and cylinder and has an antagonistic effect to that of the fluid that may be contained in the chamber 105. Therefore, it will be seen that the operation of the spring 106 opposes movement of the piston 2 to the left as viewed in FIG. 7 so as to oppose the action of the pressurized fluid in chamber 105.
  • An opening 107 made in the wall of the cylinder connects the chamber 104 to atmosphere.
  • the delivery conduit of the pump is shown at 112 and is connected only to conduits 16, 19 and 25, but on the other hand is not connected to the small chamber 104 as the conduit 12 of FIG. 1 is to chamber 4.
  • FIG. 8 shows a variant of the actual feed of pressurised fluid.
  • a pump 210 is connected to the reservoir 9 by its inlet conduit 21 l and to the chamber 4 by its delivery conduit 213. Furthermore, a conduit 237 is connected to a pressurised fluid accumulator 236. The conduits 16 and 25 are themselves connected to conduit 237, a conduit 219 connecting the restriction 21a to said conduit 16.
  • a conduit 215 connects the conduit213 toreservoir 9, a calibrated discharge valve 214 being disposed on said conduit 215.
  • FIG. 9 shows an arrangement which is similar to the one shown in FIG. 1.
  • the delivery conduit of the pump 10 referenced at 312 is no longer connected to chamber 4 but to large chamber 5.
  • the third conduit connected to the distributor 13, other than conduits and 16, is referenced at 314 and connects said distributor to small chamber 4.
  • the conduits 16, 19 and 25 are connected to conduit 312, as they were to conduit 12 of FIG. 1, in the same way as the conduits 23 and 25 are connected to conduit 314, as they were beforehand to conduit 14 of FIG. 1.
  • a spring 301 is interposed between piston 2 and the cylinder of jack 5 and has an antagonistic effect to that of the fluid that may be contained in the chamber 5. I
  • the distributor is disposed according to what is shown in FIG. 2.
  • the pressurised fluid delivered by the pump 10 is directed on the one hand through conduit 12 and on the other hand through conduits 12, 16 and 14 towards chambers 4 and 5, respectively, of jack 1.
  • the effect of this fluid on the piston 2 tends to repel this latter in the direction of arrow F.
  • the pressurised fluid reaches the inlet of the engine 18 through conduits 12 and 19, through the restriction 21. Consequently, the engine ,18 is rotated and actuates the distributor 13 in order to dispose it from its first to its second position.
  • the overall inertia of the body 6 and the rod and piston 3 of the piston 2 which are coupled thereto opposes their movement in the direction of arrow F.
  • the pressure of the fluid therefore increases in chamber 4 ofthe jack 1 and consequently in conduit 12.
  • the flow of fluid through the restriction 21 therefore increases too, this having for its effect to increase the speed of the engine 18 and to accelerate the change of position of the distributor 13. It is therefore realised that the speed of the change of position of this distributor 13 is a function of the value of the overall inertia of the body 6 coupled to the piston rod 3, or that the frequency of the movement of the body 6 is a function of the value of the overall inertia.
  • the spring 106 of the device of FIG. 7 has an effect of returning the piston 102 into position, similar to the one produced by the action of the pressurised fluid, which was contained in chamber 4 of the device of FIG. 1 on piston 2. It is therefore not necessary to describe the operation of the device of FIG. 7 which in fact is similar to that of the device of FIG. 1 or of the variant embodiment of FIG. 2 which has already been given.
  • FIG. 9 the functioning of the deviceshown in FIG. 9 is also similar to that of FIG. 1 or its variant of FIG. 2, described hereinbefore. In fact, the only differences are the reversal of the connections of conduits 312 and 314 to chamber 5 and 4 with respect to the connections of conduits 12 and 14 to chambers 4 and 5, respectively.
  • the fluid of the part of the conduit 20 included between the engine 18 and the calibrated valve 22 is maintained by said calibrated valve 22 under a certain pressure. Via conduit 23, through the non return valve 24, this fluid reaches conduit 14 and chamber 5, whilst filling in the provisory lack of fluid. The cavitation is therefore avoided. Moreover, when the distributor 13 is diposed in its first position, the pressurised fluid does not return from conduit 14 towards reservoir 9 via conduit 23, since the non return valve 24 prevents passage thereof towards said reservoir. I
  • the invention may be applied particularly to the production of vibration generators or further to the design of mechanisms for actuating vibrating teeth of the bucket of a public works machine to the mechanism for actuating a pneumatic drill.
  • a hydraulic fluid circuit system for providing pressurized control fluid to provide cyclic operation of a double-action hydraulic jack, said system including a hydraulic jack cylinder, a piston mounted in said hydraulic cylinder for reciprocation, said piston having a first face defining one side of a first chamber in said hydraulic chamber and a second face on an opposite side, said second face being smaller than said first face and defining one side of a second chamber in said hydraulic cylinder, a piston rod extending from said second face and being at least partly contained within said second chamber, said hydraulic cylinder, piston and piston rod comprising said hydraulic jack, a fluid reservoir, a distributor valve means positionable in first and second positions, a first conduit connecting said distributor valve means to one of said chambers, a second conduit connecting said distributor valve means to said fluid reservoir, a third conduit connecting said distributor valve means to a fluid accumulator which comprises a source of pressurized fluid, a conduit connecting said second chamber to the output of a pump to provide movement of said piston toward said first chamber when said first chamber is below a predetermined pressure

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Road Paving Machines (AREA)
  • Investigating Strength Of Materials By Application Of Mechanical Stress (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
US333555A 1972-02-24 1973-02-20 Hydraulic cylinder for providing reciprocation of a hydraulic jack Expired - Lifetime US3916768A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR7206315A FR2172861B1 (fr) 1972-02-24 1972-02-24

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US333555A Expired - Lifetime US3916768A (en) 1972-02-24 1973-02-20 Hydraulic cylinder for providing reciprocation of a hydraulic jack

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US (1) US3916768A (fr)
JP (1) JPS4898855A (fr)
AR (1) AR195593A1 (fr)
BE (1) BE795282A (fr)
BR (1) BR7301298D0 (fr)
DE (1) DE2309407A1 (fr)
ES (1) ES411776A1 (fr)
FR (1) FR2172861B1 (fr)
GB (1) GB1382764A (fr)
IT (1) IT979171B (fr)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4198820A (en) * 1978-08-21 1980-04-22 N L Industries, Inc. Pumping unit for a well pump
US4261249A (en) * 1978-09-08 1981-04-14 Joy Manufacturing Company Hammer
US4384455A (en) * 1980-08-11 1983-05-24 Sperry Corporation Hydraulic motor bypass apparatus
US4491055A (en) * 1981-11-02 1985-01-01 Otis Engineering Corporation Control of continuous reciprocation of a fluid power cylinder
US4526085A (en) * 1976-07-06 1985-07-02 Poclain Hydraulic loading shovels
US4571939A (en) * 1982-12-14 1986-02-25 Otis Engineering Corporation Hydraulic well pump
US4817661A (en) * 1987-10-21 1989-04-04 Howeth David F Adjustable energy output/cyclic event filter cleaning control system
US5443140A (en) * 1992-02-10 1995-08-22 Inventio Ag Method and apparatus for reducing the power required by an hydraulic elevator drive
US6295917B1 (en) * 1999-03-24 2001-10-02 Curt D. Richardson Lost motion cylinder
EP1361312A1 (fr) * 2002-05-07 2003-11-12 Husco International, Inc. Dispositif et procédé pour faire vibrer un accessoire d'un engin de travaux
WO2005106421A1 (fr) * 2004-04-30 2005-11-10 Deutz Aktiengesellschaft Dispositif hydropulse
US20100065135A1 (en) * 2006-12-22 2010-03-18 Rueb Winfried Controlling device for hydraulic consumers
CN108862089A (zh) * 2018-07-25 2018-11-23 南京奥达升智能科技有限公司 一种具有双向作用的自锁式液压千斤顶
WO2019120128A1 (fr) * 2017-12-20 2019-06-27 山东天瑞重工有限公司 Système de travail de forage de roche hydraulique enfermé

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2541795C2 (de) * 1975-09-19 1985-09-26 Helmut Dipl.-Ing. 6200 Wiesbaden Sieke Vorrichtung zum Tiefbohren
JPS5985940U (ja) * 1982-11-30 1984-06-11 株式会社島津製作所 油圧式万能試験機
JPS59193330A (ja) * 1983-04-18 1984-11-01 Caterpillar Mitsubishi Ltd キヤブ疲労試験装置
DE3631079A1 (de) * 1986-09-12 1988-03-24 Bochumer Eisen Heintzmann Ruettelsteuerung fuer einen hydraulikzylinder
DE3841369A1 (de) * 1988-12-08 1990-06-21 Kloeckner Humboldt Deutz Ag Pulshydraulik
DE4115488A1 (de) * 1991-05-11 1992-11-12 Danfoss As Hydraulischer oszillator
CN112303068B (zh) * 2020-09-24 2023-09-05 青岛石大华通科技有限公司 一种输出高频压力脉冲的装置及方法

Citations (10)

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US2550723A (en) * 1946-11-29 1951-05-01 Frank A Best Reversing valve mechanism
US2619074A (en) * 1944-11-01 1952-11-25 Deere & Co Control and diversion of exhaust pressure in hydraulic mechanisms
US2800885A (en) * 1954-12-30 1957-07-30 Ibm Hydraulic control apparatus
US2807141A (en) * 1953-06-02 1957-09-24 Don S Strader Pulsator for a hydraulic system
US2814182A (en) * 1954-11-17 1957-11-26 American Brake Shoe Co Apparatus for operating a machine element
US2917028A (en) * 1957-11-14 1959-12-15 Inst Werkzeugmaschinen Control devices for hydraulic drives
US2980079A (en) * 1958-07-01 1961-04-18 Industrikompaniet Ab Vibrator
US3334547A (en) * 1965-07-30 1967-08-08 John F Grundmann Hydraulically operated oscillator control apparatus
US3459401A (en) * 1966-08-08 1969-08-05 True Trace Corp Ditherer and tracer valve assembly
US3759144A (en) * 1970-08-17 1973-09-18 Amada Co Ltd Hydraulic actuating system for hydraulically operated bending machine

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Publication number Priority date Publication date Assignee Title
CH364395A (de) * 1957-10-19 1962-09-15 Inst Werkzeugmaschinen Verfahren und Vorrichtung zur Steuerung der Bewegung eines durch ein Druckmedium bewegten Kolbens
FR1536031A (fr) * 1967-09-06 1968-08-09 Koeppern & Co Kg Maschf Commande hydraulique

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2619074A (en) * 1944-11-01 1952-11-25 Deere & Co Control and diversion of exhaust pressure in hydraulic mechanisms
US2550723A (en) * 1946-11-29 1951-05-01 Frank A Best Reversing valve mechanism
US2807141A (en) * 1953-06-02 1957-09-24 Don S Strader Pulsator for a hydraulic system
US2814182A (en) * 1954-11-17 1957-11-26 American Brake Shoe Co Apparatus for operating a machine element
US2800885A (en) * 1954-12-30 1957-07-30 Ibm Hydraulic control apparatus
US2917028A (en) * 1957-11-14 1959-12-15 Inst Werkzeugmaschinen Control devices for hydraulic drives
US2980079A (en) * 1958-07-01 1961-04-18 Industrikompaniet Ab Vibrator
US3334547A (en) * 1965-07-30 1967-08-08 John F Grundmann Hydraulically operated oscillator control apparatus
US3459401A (en) * 1966-08-08 1969-08-05 True Trace Corp Ditherer and tracer valve assembly
US3759144A (en) * 1970-08-17 1973-09-18 Amada Co Ltd Hydraulic actuating system for hydraulically operated bending machine

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4526085A (en) * 1976-07-06 1985-07-02 Poclain Hydraulic loading shovels
US4198820A (en) * 1978-08-21 1980-04-22 N L Industries, Inc. Pumping unit for a well pump
US4261249A (en) * 1978-09-08 1981-04-14 Joy Manufacturing Company Hammer
US4384455A (en) * 1980-08-11 1983-05-24 Sperry Corporation Hydraulic motor bypass apparatus
US4491055A (en) * 1981-11-02 1985-01-01 Otis Engineering Corporation Control of continuous reciprocation of a fluid power cylinder
US4571939A (en) * 1982-12-14 1986-02-25 Otis Engineering Corporation Hydraulic well pump
US4817661A (en) * 1987-10-21 1989-04-04 Howeth David F Adjustable energy output/cyclic event filter cleaning control system
US5443140A (en) * 1992-02-10 1995-08-22 Inventio Ag Method and apparatus for reducing the power required by an hydraulic elevator drive
US6295917B1 (en) * 1999-03-24 2001-10-02 Curt D. Richardson Lost motion cylinder
EP1361312A1 (fr) * 2002-05-07 2003-11-12 Husco International, Inc. Dispositif et procédé pour faire vibrer un accessoire d'un engin de travaux
US20030209134A1 (en) * 2002-05-07 2003-11-13 Tabor Keith A. Apparatus and method for providing vibration to an appendage of a work vehicle
US6763661B2 (en) 2002-05-07 2004-07-20 Husco International, Inc. Apparatus and method for providing vibration to an appendage of a work vehicle
WO2005106421A1 (fr) * 2004-04-30 2005-11-10 Deutz Aktiengesellschaft Dispositif hydropulse
US20100065135A1 (en) * 2006-12-22 2010-03-18 Rueb Winfried Controlling device for hydraulic consumers
US8443827B2 (en) * 2006-12-22 2013-05-21 Hydac Filtertechnik Gmbh Controlling device for hydraulic consumers
WO2019120128A1 (fr) * 2017-12-20 2019-06-27 山东天瑞重工有限公司 Système de travail de forage de roche hydraulique enfermé
CN108862089A (zh) * 2018-07-25 2018-11-23 南京奥达升智能科技有限公司 一种具有双向作用的自锁式液压千斤顶

Also Published As

Publication number Publication date
DE2309407A1 (de) 1973-08-30
ES411776A1 (es) 1976-01-01
GB1382764A (en) 1975-02-05
BE795282A (fr) 1973-05-29
JPS4898855A (fr) 1973-12-14
IT979171B (it) 1974-09-30
BR7301298D0 (pt) 1974-02-19
FR2172861B1 (fr) 1975-03-21
AR195593A1 (es) 1973-10-23
FR2172861A1 (fr) 1973-10-05

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