US3552269A - Hydraulically operable linear motor - Google Patents

Hydraulically operable linear motor Download PDF

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Publication number
US3552269A
US3552269A US809902A US3552269DA US3552269A US 3552269 A US3552269 A US 3552269A US 809902 A US809902 A US 809902A US 3552269D A US3552269D A US 3552269DA US 3552269 A US3552269 A US 3552269A
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United States
Prior art keywords
cylinder
piston
line
conduit
control valve
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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
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US809902A
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English (en)
Inventor
Friedrich-Karl Arndt
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Fried Krupp AG
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Fried Krupp AG
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L25/00—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
    • F01L25/02—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means
    • F01L25/04—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means by working-fluid of machine or engine, e.g. free-piston machine
    • F01L25/06—Arrangements with main and auxiliary valves, at least one of them being fluid-driven
    • F01L25/066—Arrangements with main and auxiliary valves, at least one of them being fluid-driven piston or piston-rod being used as auxiliary valve
    • 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
    • B25D9/14—Control devices for the reciprocating piston
    • B25D9/26—Control devices for adjusting the stroke of the piston or the force or frequency of impact thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L25/00—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
    • F01L25/02—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means
    • F01L25/04—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means by working-fluid of machine or engine, e.g. free-piston machine
    • F01L25/06—Arrangements with main and auxiliary valves, at least one of them being fluid-driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/007—Reciprocating-piston liquid engines with single cylinder, double-acting piston
    • F03C1/0073—Reciprocating-piston liquid engines with single cylinder, double-acting piston one side of the double-acting piston being always under the influence of the liquid under pressure

Definitions

  • a hydraulically operable linear motor comprising a cylinder and a piston reciprocable in said cylinder and having one side connected with a piston rod extending through said cylinder so as to define on said one piston side an annular effective surface which is continuously subjected to the working pressure while the other side is alternately subjected to the working pressure and to an exhaust pressure, hydraulically operable control valve means governing the communication of said other side with the working pressure and the exhaust pressure while groove means in said cylinder at both sides of said piston and communicating with said control valve are controlled by said piston.
  • the working cylinder in view of the required axial length of the piston,'has to have at least twice the length of the piston stroke. This is particularly undesirable when a larger working stroke is necessary. Moreover, a changein the working stroke and thereby in the working 9 frequency will not be possible with constant working pressure.
  • control valve 7 for efiecting a control adjustment is efiected hydraulically, for instance, in the following manner.
  • FIG. 1 shows a longitudinal section through a first embodiment of the present invention.
  • the hydraulically operable linear motor according to the present invention is'characterized primarily in that the variable control pressure for actuating the control valve is formed in a conduit section which communicates with two'annular grooves in the working cylinder which grooves are alternately covered up by the reciprocatory piston, the conduit section also communicating with the exhaust line through a hydraulic throttle.
  • the working piston has no control edges or the like and consequently canbe so short that the working cylinder is immaterially longer than the piston stroke.
  • the present invention provides that the cross sections of the throttles are variable.
  • a change in the working stroke and thus in the working frequency is also'possible, due to the fact that, according to a further development of the invention, the working cylinder in the vicinity of that end thereof which is alternately subjected to the pressure in the pressure line is provided not only with one annular groove but with a plurality of axially serially arranged annular grooves each of which is adapted selectively to be connected with the conduit section.
  • the working cylinder 1 of the linear motor has two working chambers 2 and 3 which are separated from each other by the piston 5 connnected to the piston rod 4.
  • the end face F, of the piston 5 delimits the working chamber 2 which through the feeding passage 6 and the control valve 7 is alternately connected to the pressure line 8 or theexhaust line 9, whereas the smaller annular surface F which surface F issmaller than the surface F 1 by the cross section of the piston rod 4, delimits the work ing chamber 3.
  • the left-hand working chamber 2 communicates with the pressure line 8, piston 5 the left.
  • the necessary movement of the valve spool 10 in the p, which' builds win this conduit section 14 acts upon the left-hand end face F of the valve spool 10.
  • the right-hand end face F of the valve spool 10 which is somewhat less in cross section than the end face F is continuously subjected to the working pressure p prevailing in the pressure line 8.
  • the cylindrical inner chamber of the control valve 7 is in communication with three annular grooves 18, 19 and 20 which successively are connected with the exhaust line 9, the feeding passage 6 and the pressure line 8.
  • the valve spool 10 also has an intermediate recess 21.
  • valve spool 10 moves to the illustrated right-hand end position in which the left-hand working chamber 2 of the working cylinder is through thefeeding passage 6, the annular groove 19, the recess 21, and the annular groove 20 in communication with the pressure line 8. With lower p however, the valve spool 10 moves to its left-hand end position in which the working chamber 2 communicates through feeding passage 6, annular groove 19, recess 21, and annular groove 18 with the line 9.
  • the change in the control pressure p is brought about when the reciprocatory piston 5 in the working cylinder 1 covers the annular grooves 15 and 16 or relieves the same.
  • the change in the control pressure p is, more specifically, brought about in the following manner.
  • the lefthand working chamber 2 communicates with the pressure line 8.
  • the same pressure p prevails and since the surface F is larger than the surface F the piston 5 moves toward the right.
  • the maximum possible control pressure p is built up because the full-working pressure p, acts upon both throttles 11 and 12.
  • FIG. 2 shows another possibility of influencing the working frequency, namely by changing the piston stroke.
  • control valve 7 for increasing the control impulse is, in the manner known perse, designed as servo valve which in its turn actuates the main control valve 7 with the main control spool 10', valve 7 being similar to valve 7 but having larger dimensions.
  • a hydraulically operable linear motor which includes: a cylinder having first and second end walls respectively arranged at opposite ends of 'said cylinder, a double-acting ,control valve means to said second position,- said control valve piston-reciprocally mounted in said cylinder, a piston rod extending through one of said cylinder end walls and being connected to one side of said piston so as to form on said one side an annular piston surface, first conduit means leading into said cylinder and continuously communicating with said annular said annular piston surface for continuouslyconveying fluid pressure to said annular piston surface when said first conduit piston surface for continuously conveying fluid pressure to means is connected to a source of fluid pressure, second co'nduit means continuously communicating with the other side of said piston, controlva lve means interposed between said first and second conduit means and movable to a first position to connect said second conduit means to said first conduit means and also movable to a second position to connect said second conduit means to an exhaust, said control valve means including first surface means in continuous communication with said first conduit means and fluid pressure operable to
  • a motor'aceofiiing to claim l in which said cylinder in the 'area where said first'line-meahs lead into saidcylinder is provided with a plurality of circular grooves spaced from each other in the axial direction 'of said cylinder and'ada'pted to be successively covered bysaid pis'tonduring the movement of the latterin onea'nd-th'e same direction and also adapted selectively to be placed int'o and out of fluid communication with said first line means.
  • a motor according to claim-5 which includes a plurality of adjustable-throttle meansxassociated with said circular grooves and said firstline means adapted to communicate therewith.
  • v i I 7.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Automation & Control Theory (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Actuator (AREA)
  • Press Drives And Press Lines (AREA)
US809902A 1968-03-27 1969-03-24 Hydraulically operable linear motor Expired - Lifetime US3552269A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE1703061A DE1703061C3 (de) 1968-03-27 1968-03-27 Hydraulisch betriebener Schubkolbenmotor

Publications (1)

Publication Number Publication Date
US3552269A true US3552269A (en) 1971-01-05

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Family Applications (1)

Application Number Title Priority Date Filing Date
US809902A Expired - Lifetime US3552269A (en) 1968-03-27 1969-03-24 Hydraulically operable linear motor

Country Status (5)

Country Link
US (1) US3552269A (de)
DE (1) DE1703061C3 (de)
FR (1) FR2004864A1 (de)
GB (1) GB1219546A (de)
SE (1) SE340431B (de)

Cited By (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3774502A (en) * 1971-05-14 1973-11-27 Krupp Gmbh Hydraulic percussion device with pressure-responsive control of impact frequency
US3782246A (en) * 1969-07-11 1974-01-01 Koeppern & Co Kg Maschf Hydraulically operated vibration drives
US3782247A (en) * 1971-12-20 1974-01-01 J Klaeger Pneumatic counter balanced oil well pump actuator utilizing an improved snifter valve
US3803983A (en) * 1971-07-23 1974-04-16 Chicago Pneumatic Tool Co Reciprocating hydraulic hammer
US3863547A (en) * 1971-12-13 1975-02-04 Bbc Brown Boveri & Cie Hydraulic drive for switchgear
DE2550129A1 (de) * 1974-11-14 1976-05-26 Af Hydraulics Hydraulisch betaetigtes schlaggeraet
US3995700A (en) * 1975-10-14 1976-12-07 Gardner-Denver Company Hydraulic rock drill system
US4006665A (en) * 1974-06-11 1977-02-08 Fa. Ingenieur Gunter Klemm Spezialuntrnehmen Fur Bohrtechnik Percussion tool
US4020746A (en) * 1974-12-14 1977-05-03 Fried. Krupp Gesellschaft Mit Beschrankter Haftung Hydraulically operable linear motor
US4026193A (en) * 1974-09-19 1977-05-31 Raymond International Inc. Hydraulically driven hammer system
US4062411A (en) * 1975-12-05 1977-12-13 Gardner-Denver Company Hydraulic percussion tool with impact blow and frequency control
DE2726046A1 (de) * 1976-06-09 1977-12-15 Mitsui Shipbuilding Eng Hydraulischer hammer
US4082032A (en) * 1974-11-13 1978-04-04 Raymond International, Inc. Control of hydraulically powered equipment
US4121499A (en) * 1976-01-29 1978-10-24 The Secretary Of State For Industry In Her Britannic Majesty's Government Of The United Kingdom Of Great Britain And Northern Ireland Switching mechanism
US4342255A (en) * 1976-06-09 1982-08-03 Mitsui Engineering And Shipbuilding Co., Ltd. Oscillator actuated hydraulic impulse device
US4344353A (en) * 1979-05-14 1982-08-17 Joy Manufacturing Company Hammer
US4349075A (en) * 1978-10-19 1982-09-14 Atlas Copco Aktiebolag Hydraulically operated impact motor
US4413687A (en) * 1980-02-20 1983-11-08 Atlas Copco Aktiebolag Hydraulically operated impact device
US4419055A (en) * 1980-09-26 1983-12-06 Deere & Company Low pressure fluid supply system
US4800797A (en) * 1986-08-07 1989-01-31 Etablissements Montabert Hydraulic percussion device and method of controlling same
US5465646A (en) * 1994-02-23 1995-11-14 Mcneil (Ohio) Corporation Hydraulic motor
US5669281A (en) * 1994-12-08 1997-09-23 Etablissements Montabert Method and machine for altering the striking stroke of a percussive machine moved by a pressurized incompressible fluid
US6152013A (en) * 1996-07-25 2000-11-28 Komatsu Ltd. Hydraulically actuated breaker with lost-motion prevention device
WO2006054949A1 (en) * 2004-11-22 2006-05-26 Atlas Copco Rock Drills Ab Percussion device having an adjustable stroke length
US20090321099A1 (en) * 2006-09-13 2009-12-31 Peter Birath Percussion device, drilling machine including such a percussion device and method for controlling such a percussion device
CN105705301A (zh) * 2013-11-01 2016-06-22 建筑设备私人有限公司 气动锤装置以及与气动锤装置有关的方法
US20160318166A1 (en) * 2013-12-18 2016-11-03 Nippon Pneumatic Manufacturing Co., Ltd. Impact-driven tool
CN108006001A (zh) * 2017-12-29 2018-05-08 浙江洁普斯清洁设备有限公司 一种自动切换的往复气缸
US11084155B2 (en) * 2016-08-31 2021-08-10 Furukawa Rock Drill Co., Ltd. Hydraulic striking device

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2461633C2 (de) * 1974-12-27 1982-05-06 Ing. Günter Klemm, Spezialunternehmen für Bohrtechnik, 5962 Drolshagen Hydraulische Schlagvorrichtung
JPS6046281B2 (ja) * 1977-05-18 1985-10-15 極東開発工業株式会社 流体圧シリンダの自動往復動制御装置
GB2027483B (en) * 1978-07-29 1982-09-02 Kawasaki Heavy Ind Ltd Hydraulic reciprocating motor
DE2910946A1 (de) * 1979-03-20 1980-10-02 Siemens Ag Dosierspritze
SE442100B (sv) * 1984-04-24 1985-12-02 Atlas Copco Ab Hydrauliskt slagverk for bergborrmaskin som medger stort regleromrade for slaglengd och frekvens
DE3524414C2 (de) * 1985-04-16 1994-06-16 Mannesmann Ag Linearantrieb
JPS63501859A (ja) * 1985-12-23 1988-07-28 スペツィアルノエ、コンストルクトルスコエ　ビュ−ロ−、ギドロインブルスノイ、チェフニキ、シビルスコボ、アッジェレ−ニア、アカデミ−、ナウク、エスエスエスエル 衝撃装置
DE4019019A1 (de) * 1990-06-14 1991-12-19 Krupp Maschinentechnik Verfahren zur ermittlung charakteristischer kenngroessen eines schlagwerks und einrichtung zur durchfuehrung des verfahrens
FI104959B (fi) 1994-06-23 2000-05-15 Sandvik Tamrock Oy Hydraulinen iskuvasara
FI104960B (fi) * 1995-07-06 2000-05-15 Sandvik Tamrock Oy Hydraulinen iskuvasara
ES2259437T3 (es) * 2003-01-28 2006-10-01 Findeva Ag Batidor que funciona neumaticamente.
SE530885C2 (sv) 2007-02-23 2008-10-07 Atlas Copco Rock Drills Ab Förfarande vid slagverk, slagverk och bergborrmaskin
WO2017110793A1 (ja) * 2015-12-24 2017-06-29 古河ロックドリル株式会社 油圧打撃装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2325138A (en) * 1940-04-09 1943-07-27 Pelton Water Wheel Co Hydraulic pumping jack
DE820599C (de) * 1949-11-01 1951-11-12 Anc Ets F A Sansens Diesel Mot Schwungradlose Kolbenkraftmaschine
US2729941A (en) * 1954-04-30 1956-01-10 Axelson Mfg Company Division O Fluid actuated pumping jack
CA651732A (en) * 1962-11-06 Ingenieurburo Dipl.Ing. Friedrich Hein? Flottmann Control system for a hydraulically operated percussion device
US3412646A (en) * 1965-06-28 1968-11-26 Rufus B. Johnston Reciprocating piston type motor systems

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA651732A (en) * 1962-11-06 Ingenieurburo Dipl.Ing. Friedrich Hein? Flottmann Control system for a hydraulically operated percussion device
US2325138A (en) * 1940-04-09 1943-07-27 Pelton Water Wheel Co Hydraulic pumping jack
DE820599C (de) * 1949-11-01 1951-11-12 Anc Ets F A Sansens Diesel Mot Schwungradlose Kolbenkraftmaschine
US2729941A (en) * 1954-04-30 1956-01-10 Axelson Mfg Company Division O Fluid actuated pumping jack
US3412646A (en) * 1965-06-28 1968-11-26 Rufus B. Johnston Reciprocating piston type motor systems

Cited By (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3782246A (en) * 1969-07-11 1974-01-01 Koeppern & Co Kg Maschf Hydraulically operated vibration drives
US3774502A (en) * 1971-05-14 1973-11-27 Krupp Gmbh Hydraulic percussion device with pressure-responsive control of impact frequency
US3803983A (en) * 1971-07-23 1974-04-16 Chicago Pneumatic Tool Co Reciprocating hydraulic hammer
US3863547A (en) * 1971-12-13 1975-02-04 Bbc Brown Boveri & Cie Hydraulic drive for switchgear
US3782247A (en) * 1971-12-20 1974-01-01 J Klaeger Pneumatic counter balanced oil well pump actuator utilizing an improved snifter valve
US4006665A (en) * 1974-06-11 1977-02-08 Fa. Ingenieur Gunter Klemm Spezialuntrnehmen Fur Bohrtechnik Percussion tool
US4026193A (en) * 1974-09-19 1977-05-31 Raymond International Inc. Hydraulically driven hammer system
US4082032A (en) * 1974-11-13 1978-04-04 Raymond International, Inc. Control of hydraulically powered equipment
DE2550129A1 (de) * 1974-11-14 1976-05-26 Af Hydraulics Hydraulisch betaetigtes schlaggeraet
US4207801A (en) * 1974-11-14 1980-06-17 A. F. Hydraulics Limited Hydraulic oscillatory devices
US4020746A (en) * 1974-12-14 1977-05-03 Fried. Krupp Gesellschaft Mit Beschrankter Haftung Hydraulically operable linear motor
US3995700A (en) * 1975-10-14 1976-12-07 Gardner-Denver Company Hydraulic rock drill system
US4062411A (en) * 1975-12-05 1977-12-13 Gardner-Denver Company Hydraulic percussion tool with impact blow and frequency control
US4121499A (en) * 1976-01-29 1978-10-24 The Secretary Of State For Industry In Her Britannic Majesty's Government Of The United Kingdom Of Great Britain And Northern Ireland Switching mechanism
DE2726046A1 (de) * 1976-06-09 1977-12-15 Mitsui Shipbuilding Eng Hydraulischer hammer
US4342255A (en) * 1976-06-09 1982-08-03 Mitsui Engineering And Shipbuilding Co., Ltd. Oscillator actuated hydraulic impulse device
US4349075A (en) * 1978-10-19 1982-09-14 Atlas Copco Aktiebolag Hydraulically operated impact motor
US4344353A (en) * 1979-05-14 1982-08-17 Joy Manufacturing Company Hammer
US4413687A (en) * 1980-02-20 1983-11-08 Atlas Copco Aktiebolag Hydraulically operated impact device
EP0035005B1 (de) * 1980-02-20 1985-05-22 Atlas Copco Aktiebolag Hydraulisches Schlaggerät
US4419055A (en) * 1980-09-26 1983-12-06 Deere & Company Low pressure fluid supply system
US4800797A (en) * 1986-08-07 1989-01-31 Etablissements Montabert Hydraulic percussion device and method of controlling same
AU610513B2 (en) * 1986-08-07 1991-05-23 Etablissements Montabert Hydraulic percussion device and method of controlling same
US5465646A (en) * 1994-02-23 1995-11-14 Mcneil (Ohio) Corporation Hydraulic motor
US5669281A (en) * 1994-12-08 1997-09-23 Etablissements Montabert Method and machine for altering the striking stroke of a percussive machine moved by a pressurized incompressible fluid
US6152013A (en) * 1996-07-25 2000-11-28 Komatsu Ltd. Hydraulically actuated breaker with lost-motion prevention device
WO2006054949A1 (en) * 2004-11-22 2006-05-26 Atlas Copco Rock Drills Ab Percussion device having an adjustable stroke length
US20090321099A1 (en) * 2006-09-13 2009-12-31 Peter Birath Percussion device, drilling machine including such a percussion device and method for controlling such a percussion device
US8069928B2 (en) * 2006-09-13 2011-12-06 Atlas Copco Rock Drills Ab Percussion device, drilling machine including such a percussion device and method for controlling such a percussion device
CN105705301A (zh) * 2013-11-01 2016-06-22 建筑设备私人有限公司 气动锤装置以及与气动锤装置有关的方法
CN105705301B (zh) * 2013-11-01 2017-07-14 建筑设备私人有限公司 气动锤装置以及与气动锤装置有关的方法
US10414034B2 (en) 2013-11-01 2019-09-17 Atlas Copco Airpower, Naamloze Vennootschap Pneumatic hammer device and a method pertaining to a pneumatic hammer device
US20160318166A1 (en) * 2013-12-18 2016-11-03 Nippon Pneumatic Manufacturing Co., Ltd. Impact-driven tool
US10343272B2 (en) * 2013-12-18 2019-07-09 Nippon Pneumatic Mfg. Co., Ltd. Impact-driven tool
US11084155B2 (en) * 2016-08-31 2021-08-10 Furukawa Rock Drill Co., Ltd. Hydraulic striking device
CN108006001A (zh) * 2017-12-29 2018-05-08 浙江洁普斯清洁设备有限公司 一种自动切换的往复气缸
CN108006001B (zh) * 2017-12-29 2023-12-12 山东洁普斯自动化科技有限公司 一种自动切换的往复气缸

Also Published As

Publication number Publication date
GB1219546A (en) 1971-01-20
DE1703061A1 (de) 1972-04-13
DE1703061B2 (de) 1973-07-05
SE340431B (de) 1971-11-15
FR2004864A1 (de) 1969-12-05
DE1703061C3 (de) 1974-02-14

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