US3661216A - Impact air driven tool - Google Patents

Impact air driven tool Download PDF

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Publication number
US3661216A
US3661216A US35193A US3661216DA US3661216A US 3661216 A US3661216 A US 3661216A US 35193 A US35193 A US 35193A US 3661216D A US3661216D A US 3661216DA US 3661216 A US3661216 A US 3661216A
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United States
Prior art keywords
chisel
cylinder
driven tool
nut
valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US35193A
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English (en)
Inventor
Takanobu Yamanaka
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.)
Nippon Pneumatic Manufacturing Co Ltd
Original Assignee
Nippon Pneumatic Manufacturing Co Ltd
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
Priority claimed from JP8647669U external-priority patent/JPS4837346Y1/ja
Priority claimed from JP1887770U external-priority patent/JPS4928293Y1/ja
Priority claimed from JP1887870U external-priority patent/JPS4913420Y1/ja
Application filed by Nippon Pneumatic Manufacturing Co Ltd filed Critical Nippon Pneumatic Manufacturing Co Ltd
Application granted granted Critical
Publication of US3661216A publication Critical patent/US3661216A/en
Anticipated expiration legal-status Critical
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    • E—FIXED CONSTRUCTIONS
    • E21—EARTH OR ROCK DRILLING; MINING
    • E21B—EARTH OR ROCK DRILLING; OBTAINING OIL, GAS, WATER, SOLUBLE OR MELTABLE MATERIALS OR A SLURRY OF MINERALS FROM WELLS
    • E21B7/00—Special methods or apparatus for drilling
    • E21B7/12—Underwater drilling
    • E21B7/124—Underwater drilling with underwater tool drive prime mover, e.g. portable drilling rigs for use on underwater floors
    • 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
    • B25D9/08—Means for driving the impulse member comprising a built-in air compressor, i.e. the tool being driven by air pressure
    • 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
    • B25D9/265—Control devices for adjusting the stroke of the piston or the force or frequency of impact thereof with arrangements for automatic stopping when the tool is lifted from the working face or suffers excessive bore resistance
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63C—LAUNCHING, HAULING-OUT, OR DRY-DOCKING OF VESSELS; LIFE-SAVING IN WATER; EQUIPMENT FOR DWELLING OR WORKING UNDER WATER; MEANS FOR SALVAGING OR SEARCHING FOR UNDERWATER OBJECTS
    • B63C11/00—Equipment for dwelling or working underwater; Means for searching for underwater objects
    • B63C11/52—Tools specially adapted for working underwater, not otherwise provided for
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/065—Details regarding assembling of the tool
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/255—Switches
    • B25D2250/265—Trigger mechanism in handle

Definitions

  • ABSTRACT [30] Foreign Application Prim), Data An impact air driven tool having a cylinder including a piston member slidable therein and capable of being reciprocated by Sept. I0, 1969 Japan ..44/86476 the action of compressed air.
  • a handle cap unit is mounted on Sept. 10, 1969 Japan ..44/86477 the upper end of said cylinder, and a chisel holding unit in- Feb. 25, 1970 Japan ..45/ l 8877 cluding a chisel member slidably supported therein is mounted Feb. 25, I970 Japan ..45/l8878 0n the lower end of said cylinder.
  • a plurality of bolts are provided for fastening said cylinder, handle cap unit and chisel 521 US.
  • Cl ..E2lb 1/00 member is threaded t0 the other end of each adjacent to [58] Field ofSearch ..173 16, 17, 137439; Said chisel holding unit and has a Contact Surface on its Outer 91/265 92/128 169 periphery engageable with a supporting surface formed in a cut-out portion of the chisel holding unit whereby the relative [56] References Cited rotation of said socket member with respect to said supporting surface is restricted.
  • a stopper member for each nut has a UNITED STATES PATENTS polygonal opening through which the nut extends, and a collar member covers each nut and is held by a split pin extending J1rnerson...
  • an M 14 IMPACT AIR muvsn TOOL TI-le present invention relates to an impact air driven tool and, more particularly, to an impact hammer having within its cylinder assembly a piston operable by the compressed air for driving a chisel.
  • the present invention has been made with a view to eliminating the above-mentioned disadvantages inherent to the conventionalimpact air driven tool.
  • an object of the present invention is to provide an improved impact air driven tool wherein provision has been made for prevention of slackening of fastener members connecting various parts of said tool.
  • Another object of the present invention is to provide an improved impact air driven tool including means for cushioning the vibration generated upon striking of the piston upon the chisel holder.
  • a further object of the present invention is to facilitate smooth movements of the chisel and the piston by the improvement of a lubricator means disposed between the chisel and a bushing secured to the cylinder assembly of the impact air driven tool.
  • a still further object of the present invention is to provide improved impact air driven tool wherein the driving force of the piston during the operation of the latter is improved by removing the back pressure.
  • a still further object of the present invention is to provide an improved impact air driven tool wherein means for avoiding blank shots of said tool has been provided in order to prevent said tool from being impaired.
  • a still further object of the present invention is to provide means for enabling the impact air driven tool to be operated under water by the improvement of the design of each outlet port of said tool.
  • FIG. 1 is a longitudinal elevational view of an impact air driven tool constructed in accordance with the teachings of the present invention, with a portion thereof being broken away,
  • FIG. 2 is a longitudinal sectional view of the impact air driven tool shown in FIG. 1,
  • FIG. 3 is a top plan view of the impact air driven tool of the present invention with its bolt and nuts being broken away,
  • FIG. 4 is a bottom plan view of the impact air driven tool of the present invention showing its chisel in cross-section
  • FIG. 5 is a cross-sectional view of the impact air driven tool taken along an upper portion of a bushing for slidably receiving a chisel therethrough,
  • FIG. 6 is a front cross-sectional view of an air outlet portion of the impact air driven tool
  • FIG. 7 is a longitudinal sectional view of the impact air driven tool provided with means for removing the back pressure and means for preventing the blank shots in accordance with the teachings of the present invention.
  • FIG. 8 is a longitudinal cross-sectional view of an essential portion of the impact air driven tool shown in FIG. 7, on an enlarged scale.
  • reference numeral 11 represents a cylinder
  • 12 represents a handle cap mounted n an upper end portion of said cylinder 11, 13 on a chisel holder
  • 14 represents a chisel movably supported within said chisel holder 13
  • 15 represents a piston slidably received within said cylinder.
  • Reference numeral 16 represents bolts extending through respective holes formed on the four corners of any of said cylinder 11, said cap 12 and said holder 13, each end of said bolts 16 upwardly from cap 12 being received by the corresponding nuts 17.
  • Reference numeral 18 represents socket members each threaded to the other end of each of said bolts 16. Although in this instance as shown each of said socket members 18 is illustrated in the fonn of box nut, it may be integrally formed with the bolt 16 as desired. However, it should be noted that the socket members 18 have particular shape. That is to say, as can be understood particularly from F IG. 1 and FIG. 4, a large portion of the outer periphery a of each of said socket members 18 is circular and coaxial with the bolt 16, but the remaining portion thereof has a greater radius of curvature than the large portion of outer periphery a so that it may serve as a contact surface b.
  • the chisel holder 13 has one-side walled cut-out portions 19 extending from a lower end to an upper end at the four corners thereof through which the respective bolts 16 can be inserted.
  • Each vertical wall of the cut-out portions 19 serves as a supporting surface c, as indicated particularly in FIG. 4, which supporting surface c being inwardly curved in conformity with the outwardly curved contact surface b of each of the socket members 18 and also somewhat tapered toward the upper portion of the chisel holder 13. It will be thus understood that the rotational movement of each socket member 18 can be substantially restricted by the corresponding supporting surface c in tight contact with the contact surface b thereof.
  • the socket member 18 is integrally formed with that end of the bolt 16
  • no relative rotation of said bolt with respect to the chisel holder 13 takes place.
  • the socket member is in the form of box nut as illustrated in FIG. 1, the bolt must be rigidly threaded to said box nut or socket member to such an extent that the lower extremity thereof engages the depth of the bolt receiving hole of said box nut or socket member.
  • reference numeral 20 represents stopper members each made of metal having a sufficient thickness and having polygonal openings 21 capable of receiving the shape of the nut 17 threaded to the other end of the bolt 16.
  • each opening 21 is provided on its inner periphery with l2 V-shaped notches d, of which six V-shaped notches being corresponded to the hexagonal shape of the nut 17 while the remaining six V-shaped notches respectively having exterior angles.
  • each of said stopper members 20 has the shape of spectacles, it should be understood that any shape may be adapted as desired.
  • Reference numeral 22 thus collars each made of elastic material such as synthetic rubber and adapted to cover the nut 17 for the purpose as will be mentioned later.
  • This collar 22 has a polygonal inner surfaces in conformity with the outer shape of the nut 17, but the radial dimension of said collar is somewhat smaller than that of the nut 17.
  • each of said collars 22 is provided at its upper portion with a transverse hole through which a split pin 24 is inserted extending through the corresponding transverse hole formed in an ear portion 23 on an upper portion of each of the nuts 17 so that detachment of the collar 22 can be reliably restricted.
  • reference numeral 27 represents a cushioning member in the cylindrical form made of elastic material such as polyurethane rubber and disposed within the chisel holder 13 in such a manner as to be supported by a seat member 29 provided at the lower end of the chisel holder 13 in tight engagement with the inner peripheral surface of the latter.
  • This cushioning member 27 is provided on its outer peripheral surface with a plurality of annular grooves 28 of arched cross-section.
  • this seat member 29 is shown as disposed within the chisel holder 13 in engagement with the inner peripheral surface of the latter independently of that portion of the chisel holder. However, it may be integrally formed with that portion of the chisel holder as desired.
  • the chisel 14 is integrally formed at its intermediate portion with a flange 30 adapted to abut against an upper portion of the annular cushioning member 27 when the chisel 14 is downwardly moved.
  • the cylinder 11 is formed at its lower end with an enlarged diameter portion 31 as shown in FIG. 2, tightly receiving a bushing 32 through which an upper end portion 33 of the chisel 14 is slidably extended.
  • This bushing 32 is provided on its inner peripheral surface with a plurality of fluid passages 34 in the circumferential direction, all of said fluid passages 34 being communicated one another by vertical fluid passages 35.
  • This bushing 32 is also provided on its upper end with a groove 36 in the radial direction together with a cut-out portion 37 of suitable length as particularly shown in FIG. 5, said cut-out portion 37 being extended from an outer end of said groove 36 so that a vertical gap 38 is formed between the inner peripheral surface of the enlarged diameter portion 31 and the outer peripheral surface of the bushing.
  • THe enlarged diameter portion 31 is provided at an intermediate portion of the inner peripheral surface thereof with a lengthwisely extending recess 39, an upper portion of said recess 39 being positioned in the overlapped relation to the vertical gap 38 so as to permit fluid passage therebetween and a lower portion of said recess 39 being communicated with the lowermost fluid passage 34 by means of a through hole 40 formed in the bushing 32 so as permit fluid passage therebetween.
  • a grease nipple 41 Provided in the wall of the cylinder 11 at an intermediate position of the lengthwisely extending recess 39 through which lubricating medium such as grease can be supplied into said recess 39.
  • Reference numeral 42 represents casings each accommodating therein an underwater exhaust system and secured to the both sides of the cylinder 11 by means of fastening members such as bolts 43.
  • a valve guide 44 is formed for slidably receiving therein a valve body 45 which normally closes a port 47 or 48, formed in the wall of the cylinder 11, under the influence of a spring member 46.
  • Each of the casings for the underwater exhaust system is formed at its lower wall portion with a plurality of exhaust openings 49 which can be communicated with the port 47 or 48 through guide holes 50, formed in the valve guide 44, as the valve body 45 disengages from the port 47 or 48.
  • the handle cap 12 as hereinbefore described is provided therein with a valve mechanism 51 of the same or substantially similar construction as provided in the conventional impact hammer.
  • a valve mechanism 51 of the same or substantially similar construction as provided in the conventional impact hammer.
  • One such conventional valve is described in US. Pat. No. 3,398,801, issued Aug. 27, I968 to Eimatsu Kotone.
  • reference numerals 47 and 48 represent the port as hereinbefore described, but the port 47 is communicated with the interior of the cylinder 11 while the port 48 is communicated with the interior of the valve mechanism 51 by means of an air passage 53.
  • This air passage 53 is formed in the wall of the cylinder 11 together with another air passage 52 which communicates between the interior of said valve mechanism 51 and the interior of the cylinder 11 through a port 56 formed at an upper portion of the inner peripheral surface of the cylinder.
  • the cylinder 11 is also formed in its wall with an air passage 54 communicating between the interior of the valve mechanism 51 and a port 55 formed in said cylinder at a position below said port 48.
  • the piston 15 commences to move downwards, causing air in the lower cylinder cavity to escape to the atmosphere through the exhaust openings 49 by means of the port 47 and then the valve body 45 and at the same time air escapes from an exhaust port provided on the valve mechanism 51 through port 55 and air passage 54.
  • the compressed air in the upper cylinder cavity commences to open the valve body 45 to escape to the atmosphere through the exhaust openings 49.
  • the valve mechanism 51 is operated. It will be thus understood that the chisel 14 is driven by the piston 15 during this time.
  • valve mechanism 51 is substantially so well known by those skilled in the art that the detailed description thereof is herein omitted.
  • the impact air driven tool of the present inven tion must first be operated while in such a normal position that the tip of the chisel I4 is contacted with a subject to be hammered, for example, rock, concrete slab, or the like, and compressed air is then supplied into the handle cap 12 by means of the coupling 25.
  • a subject to be hammered for example, rock, concrete slab, or the like
  • the cushioning member 27 has been provided within the chisel holder 13. Therefore, it will thus be understood that, when the chisel is downwardly moved by the piston, it will abut against the cushioning member instead of the above-mentioned inner end portion of the chisel holder and, accordingly, the impact of the piston on the chisel does not transmit directly to said inner end portion. This involves prevention of impairment of various parts, including the bolts 16, employed in the impact air driven tool of the present invention with substantial reduction of noises.
  • This cushioning member 27 is inserted in the chisel holder 13 substantially as illustrated in FIG. 2 and, in case of wear thereof, can be easily replaced.
  • lubrication must be effected between the inner peripheral surface of the cylinder 11 and the outer peripheral surface of the piston 15 and between the outer peripheral surface of the upper end portion 33 of the chisel l4 and the inner peripheral surface of the bushing.
  • the grease nipple 41 has been provided as shown in FIG. 2, through which grease for lubrication can be supplied into the recess 39 formed in the cylinder 11.
  • an excessive amount of grease filled in the recess 39 will in turn penetrate into the fluid passages 34 and 35 by means of the through hole 40, thus oiling the contact area between the upper end portion 33 of the chisel 14 and the bushing 32.
  • This excessive amount of grease in the recess 39 will also penetrate into the gap 38, which in turn oils the upper extremity of the bushing 32 through the groove 36.
  • Lubrication at the contact area between the cylinder wall 11 and the piston 15 may be practised by a known manner, for example, wherein a suitable oiling device is provided at any desired place on a compressed air supply tubing connected to the coupling 25 so that lubricant may be mixed in and thus supplied by the compressed air to said contact area.
  • FIG. 7 and FIG. 8 in which a slightly modified impact air driven tool of the present invention is shown, the construction wherein a cylinder 61 slidably receiving a piston 64 therein, a chisel holder 63 slidably receiving a chisel 65 therein, and a handle cap 62 are rigidly connected by means of a plurality of bolts is substantially the same as hereinbefore described with reference to FIG. 1 through FIG. 6.
  • valve mechanism 66 disposed within the handle cap 62 is to be operated by compressed air supplied into said handle cap through a coupling 67 by means of a compressed air supply tubing, thereby to act to alternatively supply the compressed air into an upper cylinder cavity above the piston 64 and a lower cylinder cavity beneath said piston 64 so that the chisel 65 may be driven by the reciprocating movement of the piston within said cylinder, is substantially the same as hereinbefore fully described with reference to FIG. 1 through FIG. 6.
  • Valve mechanism 66 may be conventional, such as described in the aforementioned US. Pat. No. 3,398,801.
  • reference numeral 68 represents a control box rigidly secured to a relatively lower portion of the outer wall of the cylinder 61 and formed therein with a valve chamber, as indicated by 69 particularly in FIG. 8, in which a valve 72 is accommodated.
  • This valve 72 is biased by a spring 71 toward a valve seat formed in an inner wall within the valve chamber 69 and into which one end of a valve rod 80 is extended.
  • Reference numeral 73 represents a bushing secured at a lower position to the inner peripheral surface of the cylinder 61, through which an upper end portion 74 of the chisel 65 is slidably extended with its flange 75 designed to engage to a lower end of said bushing 73. As particularly shown in FIG. 8, this bushing 73 is formed at its upper portion with an opening 76 in register with the valve rod 80. The opening 76 receives therein an operating member or steel ball 77.
  • annular edge portion 78 of said opening adjacent to the interior of the bushing 73 is narrowed to give a diameter smaller than that of the operating member 77 so that prevention of falling of the operating member 77 into the interior of the bushing is ensured only with a portion of said member being projected toward said interior.
  • the length of said valve rod 80 must preferably correspond to a distance between one point in which one end of said rod is contacted to the valve 72 seated to the valve seat 70 and the other point in which the other end thereof is contacted with the operating member 77 as substantially shown in FIG. 8.
  • Reference numeral 81 represents an air inlet and outlet port opened in the cylinder wall at a position where the control box 68 is located, said port 81 being communicated by means of a passage 82 with a spacing defined by the valve 72 and the valve seat engaged by said valve 72.
  • a passage 83 formed in the cylinder wall and the valve chamber 69 are connected to each other by a passage 84 formed in the control box 68 so that the valve chamber is communicated with the valve mechanism 66 disposed within the handle cap 62.
  • valve chamber 85 Formed at an intermediate portion of the passage 84 within the control box is a valve chamber 85 communicating to the air outlet and inlet port 81, a portion of said valve chamber 85 adjacent to the port 81 being formed with an annular groove 86 together with a valve port 87 as substantially shown.
  • This valve chamber 85 slidably receives therein a valve spindle 88 capable of opening and closing the valve port 87 in cooperation with a spring 89 mounted around a portion of said valve spindle 88 that is narrowed to give a diameter smaller than that of the opposite portion of said valve spindle 88.
  • the spring 89 normally acts to bias the valve spindle 88 away from the valve port 87.
  • the other remaining reference numerals 91, 92, and 94 in the drawings represent an air passage communicating the annular groove 86 to the atmosphere, an air passage communicating the valve mechanism 66 to an opening 93 formed at an intermediate portion of the wall of the cylinder 61, and an exhaust port formed at an intermediate portion of the wall of the cylinder 61 for exhausting air to the atmosphere.
  • the air contained in the lower cylinder cavity is discharged to the atmosphere through the air inlet and outlet port 81 by means of the valve port 87, then the annular groove 86 and finally the air passage 91, as the piston 64 downwardly moves to the lowermost extremity of its travel.
  • the air to be thus discharged travels a relatively shorter distance and, therefore, the backpressure can advantageously be reduced as compared with the conventional impact air driven tool wherein such air is discharged to the atmosphere through such air inlet and outlet port 81 by means of such air passage 83 and then an exhaust opening formed in conventional valve mechanism 66.
  • the chisel 65 will be extended to the lowermost limit of its travel with its flange 75 engaged against a lower end portion of the chisel holder 63. While in such condition, when the piston 65 is driven, blank shot of the chisel takes place and wrong effects may be imparted on the chisel and the chisel holder. However, so long as the tool is constructed as shown in FIG. 7 and FIG. 8 in accordance with the teachings of the present invention, when the chisel is extended to the lowermost limit of its travel, the.
  • An impact air driven tool comprising a cylinder including a piston member slidably received therein and capable of being reciprocated by the action of compressed air, a handle cap unit mounted on an upper end of said cylinder, a chisel holding unit including a chisel member slidably supported therein and mounted on a lower end of said cylinder, a plurality of bolts for fastening said cylinder, handle cap unit and chisel holding unit together, and a plurality of nuts each threaded to one end of each of said bolts adjacent to said handle cap, characterized in the provision of a plurality of socket members each threaded to the other end of said bolt adjacent to said chisel holding unit and formed at a portion of its outer periphery with a contact surface engageable with a supporting surface formed in a cut-out portion of the chisel holding unit whereby the relative rotation of said socket member with respect to said supporting surface can be restricted, a plurality of stopper members each having a polygonal opening through
  • An impact air driven tool as claimed in claim 1 further comprising a valve structure including an operating member loosely received in a lower wall of said cylinder unit and capable of being backwardly collapsed as an upper end portion of the chisel upwardly travels within the cylinder unit and being projected as said end portion of the chisel downwardly travels within the cylinder unit, said operating member while in said backwardly collapsed state permitting the opening of a fluid channel for supply of compressed air into a lower cavity below said piston within the cylinder unit.
  • An impact air driven tool as claimed in claim 1 further comprising an exhaust opening communicating to the atmosphere and formed at a position adjacent to an air outlet and inlet port formed at a lower portion of said cylinder unit and a valve structure disposed at an intermediate position between said outlet and inlet port and said exhaust opening and capable of communicating therebetween only when the gas in the cylinder unit is to be discharged.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Fluid Mechanics (AREA)
  • Mining & Mineral Resources (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Automation & Control Theory (AREA)
  • Environmental & Geological Engineering (AREA)
  • Ocean & Marine Engineering (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Percussive Tools And Related Accessories (AREA)
US35193A 1969-09-10 1970-05-06 Impact air driven tool Expired - Lifetime US3661216A (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP8647669U JPS4837346Y1 (https=) 1969-09-10 1969-09-10
JP8647769 1969-09-10
JP1887770U JPS4928293Y1 (https=) 1970-02-25 1970-02-25
JP1887870U JPS4913420Y1 (https=) 1970-02-25 1970-02-25

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US3661216A true US3661216A (en) 1972-05-09

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US (1) US3661216A (https=)
DE (1) DE2029512C3 (https=)
FR (1) FR2060507A5 (https=)
GB (1) GB1306265A (https=)
NL (1) NL7013182A (https=)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3782483A (en) * 1971-11-15 1974-01-01 Vulcan Iron Works Percussion hammer
US4327807A (en) * 1978-09-19 1982-05-04 Maco-Meudon Percussion tool casing
US4474248A (en) * 1981-04-23 1984-10-02 Giovanni Donadio Hydraulic demolishing rock drill
US5398772A (en) * 1993-07-01 1995-03-21 Reedrill, Inc. Impact hammer
US5407018A (en) * 1994-01-10 1995-04-18 Tc Services Pneumatic impact tool having improved vibration and noise attenuation
US6561285B2 (en) * 2000-10-09 2003-05-13 Sandvik Tamrock Oy Breaking apparatus and tool
US20060048957A1 (en) * 2004-09-03 2006-03-09 Sandvik Tamrock Oy Rock breaking machine and lubricating method
US20060144601A1 (en) * 2002-10-10 2006-07-06 Snap-On Incorporated Lubrification system for impact wrenches
US20060243528A1 (en) * 2005-04-27 2006-11-02 Caterpillar Inc. Lubrication system for a hydraulic or pneumatic tool
US20090025949A1 (en) * 2007-07-24 2009-01-29 Makita Corporation Power tool
US20100155097A1 (en) * 2008-12-19 2010-06-24 Credo Technology Corporation Cellular foam bumper for nailer
US8689940B2 (en) 2010-08-19 2014-04-08 Caterpillar Inc. Lubrication system for a breaking tool
US20140102740A1 (en) * 2012-10-12 2014-04-17 Caterpillar Inc. Front Head Nut Pocket Configuration for Hydraulic Hammer
US9010493B2 (en) 2012-03-13 2015-04-21 Caterpillar Inc. Lubrication arrangement
US9217341B2 (en) 2013-08-15 2015-12-22 Caterpillar Inc. Lubrication system for tool
US11413734B2 (en) * 2018-10-17 2022-08-16 Kyocera Senco Industrial Tools, Inc. Working cylinder for power tool with piston lubricating system
US12280482B2 (en) * 2022-10-25 2025-04-22 Basso Industry Corp. Driving device for electric nail gun

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RU2263019C2 (ru) * 2003-05-16 2005-10-27 Открытое Акционерное Общество "Институт Механизированного Инструмента" (ВНИИСМИ) Устройство крепления рабочего инструмента в ударной машине

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US1637192A (en) * 1926-08-26 1927-07-26 Ingersoll Rand Co Percussive tool
US1703839A (en) * 1919-05-05 1929-02-26 Sullivan Machinery Co Motor
US1713784A (en) * 1927-09-30 1929-05-21 Ingersoll Rand Co Pneumatic tool
US2290256A (en) * 1940-11-04 1942-07-21 Eugene H Souter Pneumatic tool
US2337351A (en) * 1942-11-24 1943-12-21 Worthington Pump & Mach Corp Percussive tool
US3136223A (en) * 1962-01-09 1964-06-09 Ohio Brass Co Fluid motor
US3547207A (en) * 1968-11-07 1970-12-15 Vulcan Iron Works Percussion hammer
US3559539A (en) * 1969-09-22 1971-02-02 Sp Mfg Corp Fluid actuator construction

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1703839A (en) * 1919-05-05 1929-02-26 Sullivan Machinery Co Motor
US1637192A (en) * 1926-08-26 1927-07-26 Ingersoll Rand Co Percussive tool
US1713784A (en) * 1927-09-30 1929-05-21 Ingersoll Rand Co Pneumatic tool
US2290256A (en) * 1940-11-04 1942-07-21 Eugene H Souter Pneumatic tool
US2337351A (en) * 1942-11-24 1943-12-21 Worthington Pump & Mach Corp Percussive tool
US3136223A (en) * 1962-01-09 1964-06-09 Ohio Brass Co Fluid motor
US3547207A (en) * 1968-11-07 1970-12-15 Vulcan Iron Works Percussion hammer
US3559539A (en) * 1969-09-22 1971-02-02 Sp Mfg Corp Fluid actuator construction

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3782483A (en) * 1971-11-15 1974-01-01 Vulcan Iron Works Percussion hammer
US4327807A (en) * 1978-09-19 1982-05-04 Maco-Meudon Percussion tool casing
US4474248A (en) * 1981-04-23 1984-10-02 Giovanni Donadio Hydraulic demolishing rock drill
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Also Published As

Publication number Publication date
NL7013182A (https=) 1971-03-12
DE2029512C3 (de) 1974-08-15
FR2060507A5 (https=) 1971-06-18
DE2029512A1 (de) 1972-01-27
DE2029512B2 (de) 1974-01-24
GB1306265A (https=) 1973-02-07

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