US3925985A - Impact actuator - Google Patents

Impact actuator Download PDF

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Publication number
US3925985A
US3925985A US322110A US32211073A US3925985A US 3925985 A US3925985 A US 3925985A US 322110 A US322110 A US 322110A US 32211073 A US32211073 A US 32211073A US 3925985 A US3925985 A US 3925985A
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United States
Prior art keywords
follower
impact member
drive
actuator
piston
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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 - Lifetime
Application number
US322110A
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English (en)
Inventor
Carl R Peterson
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Rapidex Inc
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Rapidex Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Rapidex Inc filed Critical Rapidex Inc
Priority to US322110A priority Critical patent/US3925985A/en
Priority to AU64120/74A priority patent/AU481281B2/en
Priority to BR85/74A priority patent/BR7400085D0/pt
Priority to CA189,686A priority patent/CA992432A/en
Priority to SE7400275A priority patent/SE399200B/sv
Priority to FR7400706A priority patent/FR2325294A7/fr
Priority to GB105774A priority patent/GB1446096A/en
Priority to DE2400925A priority patent/DE2400925A1/de
Priority to JP49005416A priority patent/JPS4998701A/ja
Application granted granted Critical
Publication of US3925985A publication Critical patent/US3925985A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J7/00—Hammers; Forging machines with hammers or die jaws acting by impact
    • B21J7/20—Drives for hammers; Transmission means therefor
    • B21J7/22—Drives for hammers; Transmission means therefor for power hammers
    • B21J7/28—Drives for hammers; Transmission means therefor for power hammers operated by hydraulic or liquid pressure
    • 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
    • E02D7/02—Placing by driving
    • E02D7/06—Power-driven drivers
    • E02D7/10—Power-driven drivers with pressure-actuated hammer, i.e. the pressure fluid acting directly on the hammer structure

Definitions

  • ABSTRACT Actuators capable of repeated impacts in which a hydraulically driven follower follows the expansibly driven impact member. Also shown are constant input and output hydraulic flows valved alternately between an impact member returning motion which recompresses the expansible drive, and a following motion causing the follower to follow the suddenly accelerated impact member. The follower is shown to control these flows by means of a slave valve operated by changes of pressure attributable to the position of the parts.
  • a stationary tube between the linear piston and the moving follower sleeve separates the follower drive chamber from the expansible medium in one illustrated embodiment and a follower drive chamber formed along the side of the piston is featured in another illustratron.
  • the present invention relates to impact delivering devices as might be used for rock drilling, pavement breaking, forging, pile driving, impact wrenches, etc., and in particular to such devices as powered by high pressure hydraulic fluid.
  • Actuators capable of delivering repeated impacts to a variable position, whether in straight or rotary motion, are known.
  • Those to which the present invention relates are of the type in which an elastic or expansible drive, e.g. a trapped volume of pre-compressed air or a spring, is exposed to the impact member to drive it.
  • Countervailing hydraulic pressure controlled by the follower is used in the cycle to return the impact member and recompress the expansible drive prior to initiation of the next impact. It is known to return the follower with the impact member and to employ automatic triggering arrangements.
  • One such known arrangement involves venting of the hydraulic return fluid when the impact member reaches the return position' whereby restraint upon the expansible drive is suddenly removed.
  • the invention features use of hydraulic drive for the follower as it follows the impact member, and use of a hydraulic system including a positive displacement constant flow rate source of hydraulic fluid, which alternately is caused to drive the impact member in its return direction and the follower in its following direction.
  • Preferred embodiments of the invention feature: a trigger effective to release the impact member and actuate the separate motion of the follower, preferably the trigger in the form of a hydraulic vent; use of return drive pressure to hold a directional slave valve to vent the follower drive while causing the return of the impact member; and employing the trigger vent-reduced pressure to reverse the valves, to apply pressure to the follower while venting the impact member return system.
  • a trigger effective to release the impact member and actuate the separate motion of the follower, preferably the trigger in the form of a hydraulic vent
  • use of return drive pressure to hold a directional slave valve to vent the follower drive while causing the return of the impact member
  • employing the trigger vent-reduced pressure to reverse the valves, to apply pressure to the follower while venting the impact member return system.
  • Preferred embodiments feature a linear actuator construction of simple design. Other features are mentioned in the Abstract.
  • the present invention can achieve nominally constant flow rates in both inlet and discharge lines at all times. Its sleeve or valving unit, being positively driven in both directions, permits higher frequency operation. It may utilize gas or other energy storage mechanisms at pressures higher than hydraulic fluid pressure, thus allowing a smaller energy storage device or chamber.
  • FIG. 1 is a cross section of the presently preferred embodiment of the invention.
  • FIGS. 2a-d are similar cross-sections at different times in the operating cycle.
  • FIG. 3 is a similar cross-section for the special case of piston overtravel.
  • FIG. 4 is a partial view of an alternate construction of the top of the unit of FIG. 1.
  • the device consists of a housing 11, a piston 10, and a sleeve 12.
  • the piston is generally rod-like and of constant diameter except for an enlargement 10a in the center.
  • a relatively thinwalled tube 13 extends from the housing and its inner surface makes a sliding seal with the upper portion of the piston. Gas is stored in chamber 14 defined by this tube 13, the housing 11, and the top of the piston 10. Gas charging valve is shown at 15, where gas is injected into chamber 14 at intervals to make up for leakage from chamber 14.
  • the movable sleeve 12 slidingly seals on the outer surface of tube 13 and the inner surface of housing 11.
  • the sleeve 12 is flared at 12a at its lower end and shaped to seal against the piston enlargement at 16.
  • the sleeve contains a number of longitudinal internal holes 17, communicating radially through short holes 17a with its outer surface at 18.
  • a number of external short, axially extending slots, 19, are provided in the sleeve in such position as not to communicate with holes 17.
  • the piston 10, piston enlargement 10a, sleeve 12, and tube 13, define an annu lar volume of fluid at 20.
  • the housing 11 includes an upper bore 11a, sized to seal slidingly with the sleeve 12 and a second, next lower bore 11b of enlarged diameter making no seals with any moving parts.
  • the housing has a bore lle of larger dimension than those above, defining a region for free axial movement of the enlargement 10a of the piston, and of the flared end 12a of piston 12, with ample space S for displacementof fluid about the periphery of these members when they move.
  • the lower-most bore 11f of the housing slidingly seals against the piston.
  • the housing contains a lower port, 23, communicat ing with the enlarged lower housing volume 23", a vent, 24, communicating with the volume 22, and an upper port 25, communicating with volume 15'', the volume above the sleeve 12.
  • the volume 14 is filled with gas to the desired pressure. Except for leakage, this operation is not repeated.
  • the unit is combined with an ordinary two-position reversing valve shown schematically at 26. It contains an internal shuttling member or spool 27 that is biased upwardly by springs at 28.
  • the valve is connected to a pump 29 of the positive displacement, constant flow type, through line 30, and to a return reservoir (not shown) through line 31.
  • Opposite ends of the valve spool 27 are pressurized from these two lines through lines 30' and 31'.
  • the valve is connected to the hammer as shown with line 23 to port 23 and volume 23", line 25 to port 25 and volume 25". Vent 24 is connected through line 24' to the reservoir line 31.
  • volume 20 between sleeve and piston, is at low pressure, sealed from 23" at 16 (FIG. 1) and vented through holes 17, 17a, 18, volume 22, port 24 and line 24 to the reservoir. Volume 25 is also vented to the reservoir.
  • the outer diameter of the main body of sleeve 12 is less than the diameter of the seal at 16, hence there is a net downward force acting upon the upper surface of the flare 12a, holding the sleeve to the piston as suggested by arrows at 32.
  • the net effect is a reduction in pressure in volume 23" and an increase in pressure in volume 20 until the net force acting across piston enlargement 10a is no longer sufficient to hold the piston 10 upward against gas pressure in volume 14, albeit sleeve 12 still moves upwardly due to pressure differential across it caused by continued inflow to volume 23".
  • the seal at 16 is thus broken and the pressure differential across enlargement 10a is completely destroyed.
  • the piston is thus triggered” and free to move downward rapidly under the influence of compressed gas in volume 14, here without any displacement of hydraulic fluid from volume 23" because the two ends of the piston are of equal diameter. Once seal 16 is broken, pressures in volumes 23 and 25" tend to equalize across the equal area ends of sleeve 12.
  • FIG. 3 illustrates the special case when the bit 50 at the end of the piston has dropped away and the piston overtravels to the position shown, stopped by a mechanical stop (with snubbing action) shown schematically at 40.
  • a mechanical stop with snubbing action
  • FIG. 3 illustrates the special case when the bit 50 at the end of the piston has dropped away and the piston overtravels to the position shown, stopped by a mechanical stop (with snubbing action) shown schematically at 40.
  • a mechanical stop with snubbing action
  • an integral housing casting 11' which forms the bores 11a and 1 lb, etc., has an uppermost bore 11g above and of smaller diameter than bore 11a.
  • a constant diameter portion of piston extends entirely through sleeve 12 into sealing contact with bore 11g throughout the operating range, forming compressed gas chamber 14.
  • the dashed lines of FIG. 4 illustrate an automatic filling arrangement useful when volume 14 is sized to receive hydraulic fluid to provide a hydraulic spring for driving the impact member.
  • the upper dashed line receives fluid from the pump (line 30) through check valve 14.
  • the lower dashed line leads to vented discharge. This vent is positioned just below the piston top edge when the piston is at its normal impact point. This will enable volume 14 to be vented as the piston returns from an abnormally low position (as in FIG. 3), and thereby sets the maximum amount of hydraulic fluid trapped in volume 14, and thus avoids build-up of excess pressure in volume 14 during operation.
  • the construction shown in FIG. 4, in which volume 14 is formed by the housing can be made very ruggedly and is suitable for the pressures associated with use of hydraulic fluid as the spring for driving the impact member.
  • a radially floating separately formed stationary tube 13 could be employed; instead of compressed gas other compressible material or mechanism could act upon the piston or hydraulic fluid as just mentioned; the ends of the piston could be of different area with provision for flow of displaced fluids; the entire reciprocating structure could be of rotary rather than linear arrangement; all fluid can be made to exit chamber 23 through hole 17 and port 24, etc.
  • an actuator capable of delivering repeated impacts to a variable, stopped position comprising the combination of an impact member movable back and forth relative to said position, an expansible drive for driving said member toward said position while expanding, and a return for returning said impact member and recompressing said drive, said return including a follower which follows said impact member to its variable stopped position and a hydraulic system enabled by said position of said follower to apply return force to said impact member, the improvement wherein said hydraulic system includes a hydraulic drive for said follower in the following direction, a valve separate from said follower and impact member effective to direct said flow alternately to drive said follower in following direction and drive said impact member in its return direction and a control for actuating said follower drive upon said driving of said impact member.
  • said hydraulic system includes a source of hydraulic fluid which comprises a positive displacement constant flow pump and said impact member has a constant cross-section at its opposite end regions whereby movement of said impact member does not displace hydraulic fluid.
  • the actuator of claim 1 including a trigger, said follower being returnable by said hydraulic fluid with said impact member, and said trigger being effective both to release said impact member to be driven by said expansible drive and to actuate said control for separate following motion of said follower drive.
  • said trigger comprises a vent opened by said impact member and follower reaching said return position, said vent operable both to relieve the net hydraulic return pressure upon said impact member to the point where it is overcome by said expansible drive and to actuate said control.
  • valve is held in a first position by pressure returning said impact member, the valve effective to admit return fluid to said impact member and to vent said follower drive, and said vent effective, through relief of return pressure, to operate said valve to a second position to apply hydraulic pressure to and control said follower drive.
  • valve is operative in said second position to apply the pressure of said follower drive to said valve upon buildup of pressure in said follower drive associated with said follower reaching said impact member, said pressure operative to reverse said valve to said first position.
  • said trigger is formed by mating portions of said follower and impact member providing a seal when seated and creating pressure conditions whereby said impact member and follower are returned as a unit, and in the return position said vent operative to break said seal and expose a surface of said impact member to forces concelling return forces.
  • the actuator of claim 10 in the form of a linear actuator wherein said impact member comprises a reciprocable piston having an enlarged middle portion, said follower comprises a sleeve linearly telescopically fitted about the exterior of said piston, having a flared end engageable upon said enlarged middle portion of said piston and having an oppositely directed surface exposed to said hydraulic follower drive.
  • the actuator of claim 11 including a housing forming a first chamber into which said piston and flared end of said sleeve extend, a first hydraulic line connected thereto for said hydraulic return, a second chamber to which said oppositely directed surface of said follower is exposed, a second hydraulic line connected thereto for said follower drive, a third chamber intermediate said first and second chambers and normally sealed therefrom, a third hydraulic line connected thereto for venting, a passage extending from said third chamber to the space between said flared end of said sleeve and said enlarged portion of said piston, and a vent passage in the exterior of said sleeve positioned so that when the sleeve is in its return position, said first chamber is vented to said third chamber.
  • the actuator of claim 12 including a positive displacement, constant flow hydraulic pump and a valve effective alternately to direct flow to said second line and exhaust from said first line and vice versa.
  • the actuator of claim 1 in the form of a linear actuator wherein said impact member comprises a linear piston, a stationary tube in which the inner end of said piston is fitted, the inner end of said piston and the interior of said tube cooperating to form a volume for an expansible gas drive and said follower comprising a sleeve slidably engaged upon the exterior of said tube and forming therewith a hydraulic chamber for said follower drive.
  • said actuator of claim 1 in the form of a linear actuator wherein said impact member comprises a linear piston, said follower comprising a sleeve slidably engaged upon the exterior of said piston, said housing and a portion of the side of said piston forming a hydraulic chamber for said follower drive, said piston extending beyond said chamber in sealed relation into a further chamber, the end of said piston disposed in said further chamber and exposed therein to an expansible fluid drive.
  • said impact member comprises a linear piston
  • said follower comprising a sleeve slidably engaged upon the exterior of said piston, said housing and a portion of the side of said piston forming a hydraulic chamber for said follower drive, said piston extending beyond said chamber in sealed relation into a further chamber, the end of said piston disposed in said further chamber and exposed therein to an expansible fluid drive.
  • the actuator of claim 1 in the form of a linear actuator wherein said impact member comprises a linear piston including a housing defining a bottoming position for said impact member in the absence of a workpiece at the impactreceiving position, said follower and housing cooperatively constructed to vent said follower drive prior to said follower reaching said impact member in said bottoming position, thereby preventing said follower from reaching the position for enabling application of return forces to said piston.
  • An actuator capable of delivering repeated impacts to a variable position comprising the combination of an impact member movable back and forth relative to said position, an expansible fluid drive for driving said member toward said position while expanding, and a return for returning said impact member and recompressing said drive, said drive consisting of a volume of fluid connected through a check valve to a supply of makeup fluid to allow inflow to said volume of fluid but not outflow from said volume of fluid, and a vent from said volume of fluid opened by said impact member upon overtravel beyond a predetermined position and closed by said impact member upon return travel back to said predetermined position said vent thereby being adapted to vent excess fluid at low pressure before it is recompressed by return motion of said impact member whereby said vent is effective to limit the maximum quantity of fluid trapped as said volume of fluid.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Fluid Mechanics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Paleontology (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Placing Or Removing Of Piles Or Sheet Piles, Or Accessories Thereof (AREA)
  • Actuator (AREA)
US322110A 1973-01-09 1973-01-09 Impact actuator Expired - Lifetime US3925985A (en)

Priority Applications (9)

Application Number Priority Date Filing Date Title
US322110A US3925985A (en) 1973-01-09 1973-01-09 Impact actuator
AU64120/74A AU481281B2 (en) 1973-01-09 1974-01-02 Impact actuator
CA189,686A CA992432A (en) 1973-01-09 1974-01-08 Impact actuator
BR85/74A BR7400085D0 (pt) 1973-01-09 1974-01-08 Aperfeicoamentos em servo-motor iniciador de impacto
SE7400275A SE399200B (sv) 1973-01-09 1974-01-09 Anordning for avgivande av slag
FR7400706A FR2325294A7 (fr) 1973-01-09 1974-01-09 Dispositif hydraulique de declenchement de percussions
GB105774A GB1446096A (en) 1973-01-09 1974-01-09 Impact actuator
DE2400925A DE2400925A1 (de) 1973-01-09 1974-01-09 Schlagvorrichtung
JP49005416A JPS4998701A (sv) 1973-01-09 1974-01-09

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US322110A US3925985A (en) 1973-01-09 1973-01-09 Impact actuator

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US3925985A true US3925985A (en) 1975-12-16

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US322110A Expired - Lifetime US3925985A (en) 1973-01-09 1973-01-09 Impact actuator

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US (1) US3925985A (sv)
JP (1) JPS4998701A (sv)
BR (1) BR7400085D0 (sv)
CA (1) CA992432A (sv)
DE (1) DE2400925A1 (sv)
FR (1) FR2325294A7 (sv)
GB (1) GB1446096A (sv)
SE (1) SE399200B (sv)

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4022108A (en) * 1974-04-20 1977-05-10 Linden-Alimak Ab Hydraulically operated percussion device
US4062411A (en) * 1975-12-05 1977-12-13 Gardner-Denver Company Hydraulic percussion tool with impact blow and frequency control
US4077608A (en) * 1977-01-04 1978-03-07 Auto Specialties Manufacturing Company Hydraulic hand jack
US4077304A (en) * 1976-03-15 1978-03-07 Hydroacoustics Inc. Impact tools
US4231434A (en) * 1978-02-21 1980-11-04 Justus Edgar J Hydraulic impact device
US4344353A (en) * 1979-05-14 1982-08-17 Joy Manufacturing Company Hammer
US4363258A (en) * 1980-04-17 1982-12-14 Joy Manufacturing Company Hydraulic impactor
US4380901A (en) * 1979-06-29 1983-04-26 Kone Oy Hydraulic percussion machine
US4479551A (en) * 1981-11-27 1984-10-30 Hughes Tool Company Actuator for a hydraulic impact device
US4512417A (en) * 1981-11-05 1985-04-23 Ingersoll-Rand Company Hydraulic reciprocating device
US4563941A (en) * 1983-09-16 1986-01-14 Danfoss A/S Hydraulic actuator for control of valves
US4577547A (en) * 1982-07-27 1986-03-25 Jaworski Bill L Impact tool
US4784371A (en) * 1987-07-16 1988-11-15 Hein-Werner Corporation Hydraulic jack having a small diameter bleed part in the cylinder wall
US5038668A (en) * 1989-04-27 1991-08-13 Krupp Maschinentechnik Gmbh Hydraulic striking mechanism
US5765462A (en) * 1995-04-26 1998-06-16 Valmet Corporation Web cutting device
WO1999019096A1 (de) * 1997-10-15 1999-04-22 Sms Eumuco Gmbh Hydraulisches antriebssystem für stössel von schmiedepressen oder schmiedemaschinen
WO2003097945A1 (en) * 2002-05-17 2003-11-27 Raunisto Yrjoe A device producing hammering
US6658972B1 (en) * 1999-06-24 2003-12-09 Heidelberger Druckmaschinen Ag Full force web severer
US20050145400A1 (en) * 2003-12-19 2005-07-07 Clark Equipment Company Impact tool
US20050175487A1 (en) * 2002-05-17 2005-08-11 Reijo Malefelt Hudraulic hammer with control means regulating the volume in an accumulator
US20160288306A1 (en) * 2015-04-06 2016-10-06 Caterpillar Inc. Hydraulic hammer having self-contained gas spring
US20180010389A1 (en) * 2015-03-27 2018-01-11 Charles Abernethy Anderson Apparatus and method for modifying axial force
RU208326U1 (ru) * 2021-06-25 2021-12-14 Федеральное государственное бюджетное учреждение науки Институт горного дела им. Н.А. Чинакала Сибирского отделения Российской академии наук (ИГД СО РАН) Устройство ударного действия
WO2023086607A1 (en) * 2021-11-12 2023-05-19 Innovex Downhole Solutions, Inc. Downhole artificial lift assembly
US11730553B2 (en) * 2013-08-05 2023-08-22 Intuitive Surgical Operations, Inc. Devices, systems, and methods for surgical instrument reprocessing

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5819433B2 (ja) * 1977-03-17 1983-04-18 日本ニユ−マチツク工業株式会社 衝撃動工具
US4256187A (en) * 1978-11-30 1981-03-17 Hughes Tool Company Impact tool with hydraulic cocking mechanism
DE3030910A1 (de) * 1979-08-17 1981-03-26 Dobson Park Industries Ltd., Nottingham, Nottinghamshire Schlagendes oder stossendes werkzeug
DE2933640C2 (de) * 1979-08-20 1985-05-15 Edgar J. Beloit Wis. Justus Hydraulische Schlagvorrichtung
JPH0236080A (ja) * 1988-07-26 1990-02-06 Nippon Pneumatic Mfg Co Ltd 衝撃動装置
ATE145028T1 (de) * 1992-01-21 1996-11-15 Bsp Int Foundation Ventilsteuervorrichtung

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1429786A (en) * 1920-08-13 1922-09-19 Ingersoll Rand Co Rock drill
US1626087A (en) * 1925-04-23 1927-04-26 Charles A Hultquist Fluid-operated percussive tool
US2997849A (en) * 1959-05-28 1961-08-29 Outboard Marine Corp Self-purging hydraulic control device
US3411592A (en) * 1965-01-28 1968-11-19 Montabert Roger Percussion apparatus
US3524385A (en) * 1966-07-11 1970-08-18 Impulse Prod Corp Control means for fluid-powered devices
US3583158A (en) * 1968-01-12 1971-06-08 Nat Res Dev Transducer for converting fluid pressure oscillations into mechanical oscillations
US3595133A (en) * 1968-07-02 1971-07-27 Nat Res Dev Transducer for producing mechanical oscillations
US3687008A (en) * 1971-02-01 1972-08-29 W J Savage Co Inc Pressure fluid controlled reciprocating mechanism
US3735823A (en) * 1970-05-01 1973-05-29 Nippon Pneumatic Mfg Impact motive implement
US3796050A (en) * 1972-05-18 1974-03-12 Foster Miller Ass High energy rate actuator
US3800664A (en) * 1971-02-10 1974-04-02 Dobson Park Ind Impact tools or apparatus

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1429786A (en) * 1920-08-13 1922-09-19 Ingersoll Rand Co Rock drill
US1626087A (en) * 1925-04-23 1927-04-26 Charles A Hultquist Fluid-operated percussive tool
US2997849A (en) * 1959-05-28 1961-08-29 Outboard Marine Corp Self-purging hydraulic control device
US3411592A (en) * 1965-01-28 1968-11-19 Montabert Roger Percussion apparatus
US3524385A (en) * 1966-07-11 1970-08-18 Impulse Prod Corp Control means for fluid-powered devices
US3583158A (en) * 1968-01-12 1971-06-08 Nat Res Dev Transducer for converting fluid pressure oscillations into mechanical oscillations
US3595133A (en) * 1968-07-02 1971-07-27 Nat Res Dev Transducer for producing mechanical oscillations
US3735823A (en) * 1970-05-01 1973-05-29 Nippon Pneumatic Mfg Impact motive implement
US3687008A (en) * 1971-02-01 1972-08-29 W J Savage Co Inc Pressure fluid controlled reciprocating mechanism
US3800664A (en) * 1971-02-10 1974-04-02 Dobson Park Ind Impact tools or apparatus
US3796050A (en) * 1972-05-18 1974-03-12 Foster Miller Ass High energy rate actuator

Cited By (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4022108A (en) * 1974-04-20 1977-05-10 Linden-Alimak Ab Hydraulically operated percussion device
US4062411A (en) * 1975-12-05 1977-12-13 Gardner-Denver Company Hydraulic percussion tool with impact blow and frequency control
US4077304A (en) * 1976-03-15 1978-03-07 Hydroacoustics Inc. Impact tools
US4077608A (en) * 1977-01-04 1978-03-07 Auto Specialties Manufacturing Company Hydraulic hand jack
US4231434A (en) * 1978-02-21 1980-11-04 Justus Edgar J Hydraulic impact device
US4344353A (en) * 1979-05-14 1982-08-17 Joy Manufacturing Company Hammer
US4380901A (en) * 1979-06-29 1983-04-26 Kone Oy Hydraulic percussion machine
US4363258A (en) * 1980-04-17 1982-12-14 Joy Manufacturing Company Hydraulic impactor
US4512417A (en) * 1981-11-05 1985-04-23 Ingersoll-Rand Company Hydraulic reciprocating device
US4479551A (en) * 1981-11-27 1984-10-30 Hughes Tool Company Actuator for a hydraulic impact device
US4577547A (en) * 1982-07-27 1986-03-25 Jaworski Bill L Impact tool
US4563941A (en) * 1983-09-16 1986-01-14 Danfoss A/S Hydraulic actuator for control of valves
US4784371A (en) * 1987-07-16 1988-11-15 Hein-Werner Corporation Hydraulic jack having a small diameter bleed part in the cylinder wall
US5038668A (en) * 1989-04-27 1991-08-13 Krupp Maschinentechnik Gmbh Hydraulic striking mechanism
US5765462A (en) * 1995-04-26 1998-06-16 Valmet Corporation Web cutting device
WO1999019096A1 (de) * 1997-10-15 1999-04-22 Sms Eumuco Gmbh Hydraulisches antriebssystem für stössel von schmiedepressen oder schmiedemaschinen
US6658972B1 (en) * 1999-06-24 2003-12-09 Heidelberger Druckmaschinen Ag Full force web severer
US20050199405A1 (en) * 2002-05-17 2005-09-15 Yrjo Raunisto Device producing hammering
WO2003097945A1 (en) * 2002-05-17 2003-11-27 Raunisto Yrjoe A device producing hammering
US20050175487A1 (en) * 2002-05-17 2005-08-11 Reijo Malefelt Hudraulic hammer with control means regulating the volume in an accumulator
US7156190B2 (en) 2003-12-19 2007-01-02 Clark Equipment Company Impact tool
US20050145400A1 (en) * 2003-12-19 2005-07-07 Clark Equipment Company Impact tool
US11730553B2 (en) * 2013-08-05 2023-08-22 Intuitive Surgical Operations, Inc. Devices, systems, and methods for surgical instrument reprocessing
US20230329814A1 (en) * 2013-08-05 2023-10-19 Intuitive Surgical Operations, Inc. Devices, systems, and methods for surgical instrument reprocessing
US20180010389A1 (en) * 2015-03-27 2018-01-11 Charles Abernethy Anderson Apparatus and method for modifying axial force
US11149495B2 (en) * 2015-03-27 2021-10-19 Charles Abernethy Anderson Apparatus and method for modifying axial force
US11619095B2 (en) 2015-03-27 2023-04-04 Charles Abernethy Anderson Apparatus and method for modifying axial force
US20160288306A1 (en) * 2015-04-06 2016-10-06 Caterpillar Inc. Hydraulic hammer having self-contained gas spring
RU208326U1 (ru) * 2021-06-25 2021-12-14 Федеральное государственное бюджетное учреждение науки Институт горного дела им. Н.А. Чинакала Сибирского отделения Российской академии наук (ИГД СО РАН) Устройство ударного действия
WO2023086607A1 (en) * 2021-11-12 2023-05-19 Innovex Downhole Solutions, Inc. Downhole artificial lift assembly

Also Published As

Publication number Publication date
AU6412074A (en) 1975-07-03
SE399200B (sv) 1978-02-06
DE2400925A1 (de) 1974-07-18
GB1446096A (en) 1976-08-11
FR2325294A7 (fr) 1977-04-15
BR7400085D0 (pt) 1974-08-15
JPS4998701A (sv) 1974-09-18
CA992432A (en) 1976-07-06

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