US3788404A - Pneumatic impact tool - Google Patents

Pneumatic impact tool Download PDF

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Publication number
US3788404A
US3788404A US00221584A US3788404DA US3788404A US 3788404 A US3788404 A US 3788404A US 00221584 A US00221584 A US 00221584A US 3788404D A US3788404D A US 3788404DA US 3788404 A US3788404 A US 3788404A
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United States
Prior art keywords
tool
working cylinder
piston
casing
pneumatic impact
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Expired - Lifetime
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US00221584A
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English (en)
Inventor
V Koudelka
M Lada
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NARADI
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NARADI
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/24—Damping the reaction force

Definitions

  • PNEUMATIC IMPACT TOOL Inventors: Vladimir Koudelka, Roztoky u Krivoklatu; Mirko Lada, Prague, both of Czechoslovakia Naradi, Narodni podnik, Prague, Czechoslovakia Filed: Jan. 28, 1972 Appl. No.: 221,584
  • ABSTRACT A penumatic impact tool, in which oscillations below the frequency of 1000 cycles per second, which are detrimental to the health of the operator, are substantially reduced by the arrangement of the working cylinder as a dilation cylinder, composed of two axially aligned parts, cushioned with respect to the body of the tool.
  • This invention relates to an arrangement in a pneumatic impact tool which solves the problem of reduction of vibrations transmitted to the handle of the tool in the course of its operation.
  • vibrations of the tool it is to be understood that there is the whole range of mechanical oscillations of the pneumatic impact tool and its parts, which oscillations are generated either as so called back strokes generated by the exciting force, or by oscillations of frequencies which although still measurable, have values of the order of ten thousands of cycles per second. Oscillations of different frequencies have different effects on an individual using the tool and their effect is determined by the capability of the individual tissues of the human body to transmit and to damp these oscillations. How far a certain frequency is detrimental to the health of individual using the tool can be determined from rules issued by health learnt from rules issued by health departments which indicate maximum acceptable levels of acceleration for each frequency or frequency range.
  • the most dangerous frequencies are the lowest, frequencies which are higher than the medium octave range at 1,000 cycles per second are not transmitted to the human body and the medical rules do not define any limitations therefor.
  • the frequencies up to the medium octave range at 1,000 cycles per second are, therefore, decisive for consideration in determining whether the tool is suitable or harmful from the medical point of view.
  • the pneumatic impact tool comprises a working cylinder arranged as a dilatation cylinder and composed of a reaction part and a guiding part, both arranged coaxially, sliding in a body, whereby both said parts, the reaction part and the guiding part are individually cushioned with respect to said body at least one prestressed elastic element, the casing with the attached handle being arranged slidingly with respect to said body and in the axial direction cushioned by at least one prestressed elastic element.
  • a particularly advantageous arrangement is one in which a damping space is provided between the front wall of the reaction part of the working cylinder and the part of the casing with the handle, facing this front wall.
  • a combined oscillating system is thus created by the pneumatic impact tool according to this invention, which system can be mathematically evaluated preferably by using an automatic calculating machine, determining the dependence between the stiffnesses of individual resilient elements and the masses of individual oscillating parts so that the resulting acceleration of the oscillating motion on the handle of the pneumatic impact tool within the whole frequency range defined by medical rules, should be a minimum. Comparing this arrangement with actually used methods for reduction of vibrations, which try to remove only the consequences of an unsuitable constructional arrangement of the tool, the arrangement according to this invention eliminates the generation of vibrations by a new construction arrangement of the impact tool.
  • both the force acting on the working cylinder by action of the pressure medium, and the back strokes of the workingtool, are not transmitted to the body in their full magnitude. Damping is also achieved by cushioning of the handle with respect to 'the body of the impact tool.
  • the mantle of the impact tool with the handle connected thereto are both, therefore, vibrated by a substantially reduced force, with the consequence reduction of the acceleration level within the frequency range indicated by medical rules.
  • the reduction of the acceleration level of oscillations within this range substantially reduces the occuran'ce of occupational diseases such as, for instance, vasoneurosis and diseases of the joints.
  • the reduction of vibrations of the tool arranged according to this invention enables a reduction of the pressing force on the pneumatic impact tool while maintaining perfect contact of the working tool with the rock, achieving a higher output of the tool with substantially reduced physical fatigue of the attendant.
  • the attendant is capable to work with full efficiency for a longer time interval than with known tools.
  • the lifetime of parts connected with the handle is simultaneously increased and requirements for their dimensions are reduced, permitting reduction in the overall weight of the tool.
  • FIG. 1 is a general schematic outline of a pneumatic impact tool in a partial, longitudinal, cross-sectional view
  • FIG. 2 is a pneumatic impact hammer shown in partial cross sectional view
  • FIG. 3 is a detailed view of the distributing means of the pressure medium in longitudinal section of the tool illustrated in FIGS. 1 and 2.
  • the working cylinder 1 of the tool is arranged as a dilatation cylinder, composed of a reaction part 2 and a guiding part 3.
  • a piston 4 is slidingly arranged in this working cylinder 1.
  • Both the reaction part 2 and the guiding part 3 are slidingly supported in a body 8.
  • Each of these parts 2 and 3 is individually cushioned with respect to the body 8 by prestressed springs 9 and 10 respectively.
  • the body 8 itself is slidingly supported in a casing 5 and cushioned with respect to this casing 5 by a prestressed spring 11.
  • the casing 5 is provided with a handle 6.
  • a bearing ring 12 is arranged between the guiding part 3 and the body 8 and a similar bearing ring 13 between the body 8 and the casing 5.
  • the guiding part 3 has on its lower external part a thread for an extension 16, which together with a bearing ring 14 limits the hub of the working tool 7, slidingly arranged in the guiding part 3 and in the extension 16.
  • the prestressed springs 9, 10, 11 create in the neutral position between the reaction part 2 and the front surface of the cavity in the casing 5 a damping space 15.
  • An inlet opening 18 for pressurized air is provided near the top of the reaction part 2, as indicated schematically in FIG. 1.
  • a similar inlet opening 19 is near the bottom of the guiding part 3 of the working cylinder 4.
  • An opening 20 corresponding to opening 18 is provided in the body 8.
  • An air escapes from the top or bottom part of the working cylinder through the gap 21 between the reaction part 2 and the guiding part 3 in the lower or upper extreme position of piston 4.
  • Corresponding openings are provided in the casing 5, in FIG. 2. They have been omitted in order not to complicate the drawing.
  • FIG. 3 shows schematically one possible arrangement of distributing means.
  • Pressurized air is introduced into the bore of an extension 17 on the top part of the casing 5 with the handle 6 (see also FIG. 1).
  • This bore terminates in a space 22 containing valve means consisting of a spring loaded ball 23 actuated by a control rod 24, which in turn is controlled through the operator by a pressure lever 25 on the handle 6 (see FIG. 1).
  • the valve means opens the passage into a channel 26, which is turn leads the pressure air over upper openings 27 and lower openings 28 into a change-over space 29, which openings 27 and 28 can be alternately opened and closed by a sliding plate 30, admitting pressurized air either into channel 31 connected with the opening 18 in the reaction part 2 (see FIG. 1) or into channel 32 connected with the opening 19 in the guiding part 3 of the working cylinder 1.
  • Pressurized medium for instance pressure air is introduced over the extension 17 and the valve means alternately to the upper part of the space created in the reaction part 2 and into the lower part of the space created in the guiding part 3 of the working cylinder 1.
  • Pressurized medium for instance pressure air is introduced over the extension 17 and the valve means alternately to the upper part of the space created in the reaction part 2 and into the lower part of the space created in the guiding part 3 of the working cylinder 1.
  • a straight line reciprocating movement of the piston 4 in the working cylinder 1 is generated. If the piston 4 is in its upper extreme position and the pressurized air starts to enter the working cylinder 1, the air urges the piston 4 to move towards its lower extreme position. Simultaneously a force F,, of oppsoite direction is generated, acting on the reaction part 2.
  • the piston 4 strikes in the lower extreme position the head of the working tool 7.
  • the top part of the piston 4 clears the gap 21 between the reaction part 2 and the guiding part 3, so that the air can escape from the space above the piston 4, simultaneously reducing pressure in channel 31 so that the sliding plate 30 closes by overpressure in channel 32 and cuts off the further supply of air to the opening 18 and opens access of air by way of channel 32 via the opening 19 below the piston 4 which is thereafter urged to move in a direction towards its upper extreme position. Simultaneously a force P of oppsite direction is generated, acting on the guiding part 3 and on the head of the working tool 7.
  • the working tool 7 is after impact of the piston 4 and after transfer of a part of the impact energy to the rock repelled back with a certain acceleration.
  • the spring is compressed and a force F generated, part of which is transmitted to the body 8.
  • the body 8 thus starts to oscillate due to the action of exciting forces F n and F,.
  • a force F,- is transmitted to the casing 5 and to the handle 6 connected therewith, said force F being proportional to the deviation of the body 8 with respect to the casing 5, and depending on the rigidity and on the damping coefficient of the spring 11 and on the oscillating frequency.
  • the resulting oscillating movement of the handle 6 depends therefore on the magnitude of the force F, and on the impedance of the hand of the operator.
  • Pneumatic impact tool comprising a substantially cylindrical body, a working cylinder located in said body, said working cylinder comprising an upper reaction part and a separate lower guiding part, both said parts being axially aligned in said body and being adapted to slide toward and away from each other, said upper and lower parts forming together a dilatation cylinder having a piston operating therein, said upper part and said lower part being individually cushioned with respect to said body by at least one prestressed elastic element respectively, an extension fixed to the lower end of the body, a working tool slidingly arranged in the lower part of the working cylinder and in said extension, said tool receiving the impact from the piston and from the lower part of said working cylinder, and means for alternately supplying and discharging a gaseous pressure medium into and from the spaces of the working cylinder above and below said piston.
  • the tool according to claim 1 including a casing having a handle, said casing being slidingly secured on the upper end of said body and axially cushioned with respect to said body by at least one prestressed elastic element.
  • Pneumatic impact tool as set forth in claim 1 wherein a damping space is located between the upper front wall of the reaction part and the part of the casing facing the front wall.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
US00221584A 1971-02-01 1972-01-28 Pneumatic impact tool Expired - Lifetime US3788404A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CS703A CS149009B1 (xx) 1971-02-01 1971-02-01

Publications (1)

Publication Number Publication Date
US3788404A true US3788404A (en) 1974-01-29

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
US00221584A Expired - Lifetime US3788404A (en) 1971-02-01 1972-01-28 Pneumatic impact tool

Country Status (8)

Country Link
US (1) US3788404A (xx)
AT (1) AT330698B (xx)
CA (1) CA944228A (xx)
CS (1) CS149009B1 (xx)
DD (1) DD95535A5 (xx)
DE (1) DE2204160C3 (xx)
GB (1) GB1361944A (xx)
SE (1) SE366239B (xx)

Cited By (39)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3847232A (en) * 1972-10-03 1974-11-12 N Klushin Pneumatic percussive tool
US3892280A (en) * 1973-10-30 1975-07-01 Nikolai Alexandrovich Klushin Portable pneumatic impact tool
US3920086A (en) * 1974-05-23 1975-11-18 Albert Adolfovich Goppen Pneumatic hammer
US3939923A (en) * 1974-01-23 1976-02-24 Demag Aktiengesellschaft Power-driven impact tool having an impact-resistant hand grip assembly
US4071094A (en) * 1973-06-21 1978-01-31 Viktor Evdokimovich Kilin Portable pneumatic percussive tool
US4203446A (en) * 1976-09-24 1980-05-20 Hellige Gmbh Precision spring lancet
WO1980001666A1 (en) * 1979-02-12 1980-08-21 Uster Spindel Motoren Maschf Pneumatic drill
US4237987A (en) * 1978-10-27 1980-12-09 Sherman Victor L Percussive tool
US4308926A (en) * 1979-05-15 1982-01-05 Etablissements Montabert S.A. Pneumatically cushioned percussion apparatus
FR2506204A1 (fr) * 1981-05-21 1982-11-26 Mo Vysshee Tekhn Outil pneumatique a percussion utilisable notamment en tant que marteau pneumatique pour la destruction par exemple de roches
FR2519575A1 (fr) * 1981-10-30 1983-07-18 Nitto Kohki Co Outil a percussion
EP0133609A1 (en) * 1983-08-01 1985-02-27 Atlas Copco Aktiebolag Pressure fluid operated impact motor
CH655682B (xx) * 1984-02-09 1986-05-15
FR2581337A1 (fr) * 1985-05-02 1986-11-07 Sorelem Perfectionnements aux brise-beton
US4776408A (en) * 1987-03-17 1988-10-11 Deutsch Fastener Corporation Pneumatic impact tool
EP0551719A1 (en) * 1991-12-17 1993-07-21 Ingersoll-Rand Company Hand-held percussive tool incorporating apparatus for reducing vibration transmission to the user
US5437339A (en) * 1992-03-18 1995-08-01 Max Co., Ltd. Air-pressure-operated implusion mechanism
US5799855A (en) * 1996-02-09 1998-09-01 Illinois Tool Works Inc. Velocity control and nosepiece stabilizer system for combustion powered tools
WO2001005558A1 (de) * 1999-07-20 2001-01-25 Robert Bosch Gmbh Bohr- oder schlaghammer
US6257352B1 (en) 1998-11-06 2001-07-10 Craig Nelson Rock breaking device
WO2003008156A1 (en) * 2001-06-26 2003-01-30 Breakers A/S Hydraulic hammer with a piston and a cyliner which move in anti-phase
US20040040729A1 (en) * 2001-07-24 2004-03-04 Gerhard Meixner Hand-held machine tool with vibration-damped handle
US20050268383A1 (en) * 2004-06-07 2005-12-08 Acsas Technology Corporation Shock balance controller
US20050269117A1 (en) * 2004-06-08 2005-12-08 Hitachi Koki Co., Ltd. Striking tool
US20050284646A1 (en) * 2004-06-04 2005-12-29 Dorin Bacila Vibration reduction apparatus for power tool and power tool incorporating such apparatus
US20070227753A1 (en) * 2006-03-31 2007-10-04 Shun Tai Precision., Ltd. Pneumatic hammer drill
US20080190632A1 (en) * 2003-12-10 2008-08-14 Wacker Construction Equipment Ag Percussion Hammer and/or Drill Hammer Comprising a Handle Which Can be Guided in a Linear Manner
US20090025949A1 (en) * 2007-07-24 2009-01-29 Makita Corporation Power tool
US20090277657A1 (en) * 2001-12-21 2009-11-12 Wacker Neuson Se Drilling and/or Striking Hammer with a Lubricating Device
US20090308627A1 (en) * 2006-10-02 2009-12-17 Kurt Andersson Percussion device and rock drilling machine
EP2251152A1 (de) * 2009-05-11 2010-11-17 Robert Bosch GmbH Handwerkzeugmaschine, insbesondere Elektrohandwerkzeugmaschine
WO2010130512A1 (de) * 2009-05-11 2010-11-18 Robert Bosch Gmbh Handwerkzeugmaschine, insbesondere elektrohandwerkzeugmaschine
US20110005789A1 (en) * 2008-04-24 2011-01-13 Ingemar Sven Johansson Fluid powered percussion tool
US20110024149A1 (en) * 2008-03-12 2011-02-03 Joachim Hecht Hand-held power tool
US20120024555A1 (en) * 2010-08-02 2012-02-02 Makita Corporation Impact tool
CN102421568A (zh) * 2009-05-11 2012-04-18 罗伯特·博世有限公司 手持式工具机、尤其是手持式电动工具机
US20160271780A1 (en) * 2015-03-19 2016-09-22 Jhih Jhong Lin Shock Absorption Device for Pneumatic Tool
US20200318307A1 (en) * 2015-05-18 2020-10-08 M-B-W, Inc. Vibration isolator for a pneumatic pole or backfill tamper
US11518017B2 (en) * 2017-12-19 2022-12-06 Hilti Aktiengesellschaft Vibration-damped hand-held power tool

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DK237280A (da) * 1980-06-02 1981-12-03 Wejra A S Fremgangsmaade til aktivering af en hydraulisk hammer samt en hammer med midler til udoevelse af fremgangsmaaden
DE3122979A1 (de) * 1981-06-10 1983-01-05 Hilti AG, 9494 Schaan Bohr- oder meisselhammer
DE3319875A1 (de) * 1983-06-01 1984-12-06 Licentia Patent-Verwaltungs-Gmbh, 6000 Frankfurt Elektropneumatischer bohrhammer
SE460349B (sv) * 1988-02-22 1989-10-02 Toernqvist Peter J T Fram- och aatergaaende roerelse alstrande apparat med tvaa vaendlaegen
DE3839207A1 (de) * 1988-11-19 1990-05-23 Hilti Ag Tragbares handgeraet mit schlagwerk
US5325929A (en) * 1991-07-09 1994-07-05 Bretec Oy Hydraulic impact hammer
SE469549B (sv) * 1991-11-04 1993-07-26 Atlas Copco Tools Ab Vibrationsdaempande organ foer ett handhaallet verktyg
DE102004021905B3 (de) * 2004-05-04 2005-11-03 Stefan Windschiegl Schwingungsdämpfer für Stemmlanzen und Druckluftwerkzeuge allgemein
DE102011121382B4 (de) 2011-12-19 2015-10-08 Festo Ag & Co. Kg Setzgerät
DE102011122938B3 (de) * 2011-12-19 2016-01-28 Festo Ag & Co. Kg Setzgerät
DE102012023966B3 (de) * 2012-12-07 2013-12-05 Festo Ag & Co. Kg Setzgerät zum Einbringen von Befestigungsmitteln in Befestigungsausnehmungen

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD48954A (xx) *
US2559478A (en) * 1948-11-22 1951-07-03 Stonefield Inc Hydraulic impact tool
DE1018819B (de) * 1952-11-20 1957-11-07 Moenninghoff Maschf Druckluft-Abbauhammer mit Rueckstossdaempfung durch ein elastisches Glied
US2899934A (en) * 1956-01-19 1959-08-18 salengro
US3451492A (en) * 1966-11-29 1969-06-24 Atlas Copco Ab Recoil vibration damped percussive machine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD48954A (xx) *
US2559478A (en) * 1948-11-22 1951-07-03 Stonefield Inc Hydraulic impact tool
DE1018819B (de) * 1952-11-20 1957-11-07 Moenninghoff Maschf Druckluft-Abbauhammer mit Rueckstossdaempfung durch ein elastisches Glied
US2899934A (en) * 1956-01-19 1959-08-18 salengro
US3451492A (en) * 1966-11-29 1969-06-24 Atlas Copco Ab Recoil vibration damped percussive machine

Cited By (54)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3847232A (en) * 1972-10-03 1974-11-12 N Klushin Pneumatic percussive tool
US4071094A (en) * 1973-06-21 1978-01-31 Viktor Evdokimovich Kilin Portable pneumatic percussive tool
US3892280A (en) * 1973-10-30 1975-07-01 Nikolai Alexandrovich Klushin Portable pneumatic impact tool
US3939923A (en) * 1974-01-23 1976-02-24 Demag Aktiengesellschaft Power-driven impact tool having an impact-resistant hand grip assembly
US3920086A (en) * 1974-05-23 1975-11-18 Albert Adolfovich Goppen Pneumatic hammer
US4203446A (en) * 1976-09-24 1980-05-20 Hellige Gmbh Precision spring lancet
US4237987A (en) * 1978-10-27 1980-12-09 Sherman Victor L Percussive tool
WO1980001666A1 (en) * 1979-02-12 1980-08-21 Uster Spindel Motoren Maschf Pneumatic drill
FR2448420A1 (fr) * 1979-02-12 1980-09-05 Uster Spindel Motoren Maschf Marteau piqueur a moyens d'amortissement des vibrations dues au recul
US4460051A (en) * 1979-02-12 1984-07-17 Spindel-, Motoren- Und Maschinenfabrik Ag Percussion drill hammer
US4308926A (en) * 1979-05-15 1982-01-05 Etablissements Montabert S.A. Pneumatically cushioned percussion apparatus
FR2506204A1 (fr) * 1981-05-21 1982-11-26 Mo Vysshee Tekhn Outil pneumatique a percussion utilisable notamment en tant que marteau pneumatique pour la destruction par exemple de roches
FR2519575A1 (fr) * 1981-10-30 1983-07-18 Nitto Kohki Co Outil a percussion
EP0133609A1 (en) * 1983-08-01 1985-02-27 Atlas Copco Aktiebolag Pressure fluid operated impact motor
CH655682B (xx) * 1984-02-09 1986-05-15
FR2581337A1 (fr) * 1985-05-02 1986-11-07 Sorelem Perfectionnements aux brise-beton
US4776408A (en) * 1987-03-17 1988-10-11 Deutsch Fastener Corporation Pneumatic impact tool
EP0551719A1 (en) * 1991-12-17 1993-07-21 Ingersoll-Rand Company Hand-held percussive tool incorporating apparatus for reducing vibration transmission to the user
US5437339A (en) * 1992-03-18 1995-08-01 Max Co., Ltd. Air-pressure-operated implusion mechanism
US5799855A (en) * 1996-02-09 1998-09-01 Illinois Tool Works Inc. Velocity control and nosepiece stabilizer system for combustion powered tools
US5897043A (en) * 1996-02-09 1999-04-27 Illinois Tool Works Inc. Velocity control and nosepiece stabilizer system for combustion powered tools
US6257352B1 (en) 1998-11-06 2001-07-10 Craig Nelson Rock breaking device
US6675908B1 (en) 1999-07-20 2004-01-13 Robert Bosch Gmbh Drilling hammer or impact hammer
WO2001005558A1 (de) * 1999-07-20 2001-01-25 Robert Bosch Gmbh Bohr- oder schlaghammer
WO2003008156A1 (en) * 2001-06-26 2003-01-30 Breakers A/S Hydraulic hammer with a piston and a cyliner which move in anti-phase
US20040040729A1 (en) * 2001-07-24 2004-03-04 Gerhard Meixner Hand-held machine tool with vibration-damped handle
US7076838B2 (en) * 2001-07-24 2006-07-18 Robert Bosch Gmbh Hand-held machine tool with vibration-damped handle
US20090277657A1 (en) * 2001-12-21 2009-11-12 Wacker Neuson Se Drilling and/or Striking Hammer with a Lubricating Device
US20080190632A1 (en) * 2003-12-10 2008-08-14 Wacker Construction Equipment Ag Percussion Hammer and/or Drill Hammer Comprising a Handle Which Can be Guided in a Linear Manner
US7322428B2 (en) 2004-06-04 2008-01-29 Black & Decker Inc. Vibration reduction apparatus for power tool and power tool incorporating such apparatus
US20050284646A1 (en) * 2004-06-04 2005-12-29 Dorin Bacila Vibration reduction apparatus for power tool and power tool incorporating such apparatus
US20050268383A1 (en) * 2004-06-07 2005-12-08 Acsas Technology Corporation Shock balance controller
US7603725B2 (en) * 2004-06-07 2009-10-20 Kerry Sheldon Harris Shock balance controller
EP1604785A3 (en) * 2004-06-08 2009-09-16 Hitachi Koki Co., Ltd. Striking tool
US20050269117A1 (en) * 2004-06-08 2005-12-08 Hitachi Koki Co., Ltd. Striking tool
US7819203B2 (en) 2004-06-08 2010-10-26 Hitachi Koki Co., Ltd. Striking tool
US20070227753A1 (en) * 2006-03-31 2007-10-04 Shun Tai Precision., Ltd. Pneumatic hammer drill
US7413030B2 (en) * 2006-03-31 2008-08-19 Shun Tai Precision Co., Ltd. Pneumatic hammer drill having vibration damping end cap
US20090308627A1 (en) * 2006-10-02 2009-12-17 Kurt Andersson Percussion device and rock drilling machine
US9016396B2 (en) * 2006-10-02 2015-04-28 Atlas Copco Rock Drills Ab Percussion device and rock drilling machine
US20090025949A1 (en) * 2007-07-24 2009-01-29 Makita Corporation Power tool
US7806201B2 (en) * 2007-07-24 2010-10-05 Makita Corporation Power tool with dynamic vibration damping
US8434565B2 (en) * 2008-03-12 2013-05-07 Robert Bosch Gmbh Hand-held power tool
US20110024149A1 (en) * 2008-03-12 2011-02-03 Joachim Hecht Hand-held power tool
US20110005789A1 (en) * 2008-04-24 2011-01-13 Ingemar Sven Johansson Fluid powered percussion tool
US8613327B2 (en) * 2008-04-24 2013-12-24 Atlas Copco Construction Tools Ab Fluid powered percussion tool
CN102421568A (zh) * 2009-05-11 2012-04-18 罗伯特·博世有限公司 手持式工具机、尤其是手持式电动工具机
WO2010130512A1 (de) * 2009-05-11 2010-11-18 Robert Bosch Gmbh Handwerkzeugmaschine, insbesondere elektrohandwerkzeugmaschine
EP2251152A1 (de) * 2009-05-11 2010-11-17 Robert Bosch GmbH Handwerkzeugmaschine, insbesondere Elektrohandwerkzeugmaschine
US20120024555A1 (en) * 2010-08-02 2012-02-02 Makita Corporation Impact tool
US8991517B2 (en) * 2010-08-02 2015-03-31 Makita Corporation Reaction force cushioning mechanism for an impact tool
US20160271780A1 (en) * 2015-03-19 2016-09-22 Jhih Jhong Lin Shock Absorption Device for Pneumatic Tool
US20200318307A1 (en) * 2015-05-18 2020-10-08 M-B-W, Inc. Vibration isolator for a pneumatic pole or backfill tamper
US11518017B2 (en) * 2017-12-19 2022-12-06 Hilti Aktiengesellschaft Vibration-damped hand-held power tool

Also Published As

Publication number Publication date
AT330698B (de) 1976-07-12
ATA73772A (de) 1975-09-15
DE2204160C3 (de) 1975-09-25
CA944228A (en) 1974-03-26
DD95535A5 (xx) 1973-02-05
SE366239B (xx) 1974-04-22
DE2204160B2 (xx) 1975-02-13
GB1361944A (en) 1974-07-30
DE2204160A1 (de) 1972-08-10
CS149009B1 (xx) 1973-05-24

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