US3918530A - Eccentric element for silencing tool and method - Google Patents

Eccentric element for silencing tool and method Download PDF

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Publication number
US3918530A
US3918530A US416232A US41623273A US3918530A US 3918530 A US3918530 A US 3918530A US 416232 A US416232 A US 416232A US 41623273 A US41623273 A US 41623273A US 3918530 A US3918530 A US 3918530A
Authority
US
United States
Prior art keywords
shaft portion
damping element
vibration damping
sleeve
tool
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
US416232A
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English (en)
Inventor
Bengt Viktor Nyholm
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.)
Atlas Copco AB
Original Assignee
Atlas Copco AB
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 Atlas Copco AB filed Critical Atlas Copco AB
Application granted granted Critical
Publication of US3918530A publication Critical patent/US3918530A/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
    • B25D17/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D17/11—Arrangements of noise-damping means
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S173/00—Tool driving or impacting
    • Y10S173/02—Sound muffling
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T279/00—Chucks or sockets
    • Y10T279/17—Socket type
    • Y10T279/17042—Lost motion
    • Y10T279/17094—Sleeve type retainer

Definitions

  • ABSTRACT A method and a means for silencing the noise gener- F [30] orelgn application Prlomy Data ated by a vibrating impact transmitting tool such as a Nov.22, 197.. Sweden "I. 15224/72 pneumatic hammer Operated Chisel, pick Spade or v ballast tamper in which an elastomeric damping ele- [52] 173/1 173/139 7 ment in saddle-like manner is clamped fast eccentri- 51 I (1] 2 181/36 279/ cally to a shaft portion of the tool by an encasing me- [58] Flrtid B251) 17/12.
  • the invention relates generally to silenced percussion tools and more particularly to silenced percussion tools of the type incorporating a shank and a working section with a shaft portion located therebetween and adapted to transmit impacts from said shank to said working section whereby the tool is caused to vibrate and to produce noise.
  • the noise is combated by a damping element contiguous with the shaft portion and affixed to the tool.
  • the damping element usually is an elastomeric sleeve which is placed around the shaft portion and kept in place by various means, for example by metallic retaining rings.
  • metallic retaining rings normally these solutions when applied to pneumatic hammer operated chisels, picks, spades and similar tools in practical operation lead to rapid destruction of the vibration dampener by reason of excessive penetration of the tool into the working material, especially if such penetration has to be combined with a bending lever movement of the tool.
  • a further disadvantage is that the prior methods for affixing the retaining rings normally have proved to be insufficient to retain the vibration dampener axially on a cylindrical smoothly shaped shaft portion.
  • the shaft portion usually has been provided with cost-increasing axial shoulders formed by the opposite ends of a recess on the tool or by a collar therearound against or around which the vibration dampener was squeezed or clamped.
  • vibration dampeners it furthermore is a time-consuming and cumbersome operation to replace a worn or destroyed vibration dampener after sharpening or reforging of the tool.
  • conventional vibration dampeners in some cases, particularly when the tool is provided with a retaining collar at the shank thereof, incorporates sleeves which for purposes of assembling the dampener have to be passed over the front portion of the tool. This precludes application of such dampeners for silencing integral tools provided with enlarged working sections such as chisels, spades and wedges.
  • Another object of the invention is to create a silenced percussion tool in which the vibration dampener in a better and more readily exchangeable way can be affixed to a smooth shaft portion of the tool without one having to provide cooperating collars or recesses for the axial retaining of the dampener thereon.
  • a further object is to create a silenced tool in which the vibration damping element is firmly retained and encased by'an undivided clamping sleeve applicable from the shank end of the tool past the retaining collar thereon.
  • a method for silencing a percussion tool by affixing a vibration damping element in contiguous relation thereto, said tool incorporating a shaft portion and a retaining collar adjacent thereto comprising slipping an undivided substantially cylindrical metallic sleeve over said vibration shaft portion past said collar, encasing said damping element between said sleeve and said shaft portion in eccentric mass relation to said shaft portion, and thereupon bending said sleeve locally at at least a portion thereof peripherally spaced from the portion of said sleeve opposite to a large mass portion of said vibration damping element and along lines extending longitudinally thereof for shrinking said sleeve radially to fixedly circumclamp said vibration damping element to shaft portion.
  • a silenced percussion tool comprising a shank, a retaining collar adjacent the shank, a working section, a shaft portion disposed between said collar and said working section for transmitting impacts therebetween whereby the tool is caused to vibrate and to produce noise, a vibration dampener on said shaft portion axially spaced from said collar and incorporating a vibration damping element which in saddle-like manner eccentrically straddles one side of said shaft portion for silencingv said noise, and means for affixing said damping element to said tool in simultaneous unilateral surface contact and eccentric mass relation thereto.
  • FIG. 1 shows an upper view of a spade tool according to the invention.
  • FIG. 2 shows a side view and FIG. 3 a fragmentary upper view of a silenced ballast tamping tool according to the invention.
  • FIG. 4 is an enlarged fragmentary longitudinal section and side view of the shaft portion of the tool in FIGS. 1-3.
  • FIG. 5 is a cross section of the tool in FIG. 4.
  • FIG. 6 shows the tool according to FIG. 1 in operation.
  • FIG. 7 shows in a fragmentary side view the shaft portion of a tool with a modified vibration dampener thereon shown in longitudinal section.
  • FIG. 8 is a cross section through the tool in FIG. 7.
  • FIG. 9 is a top view of the tool in FIG. 7.
  • FIG. 10, finally, is a cross section corresponding to FIGS. 5, 8 but through a modified tool.
  • FIGS. l-3' are provided with a shank l, a working section 2 which in FIG. 1 is a spade and in FIGS. 2, 3 a ballast tamping blade, and a shaft portion 3 located between the shank 1 and the working section 2.
  • the shank 1 receives impacts from a hammer, preferably a percussive machine such as for instance a pneumatic hammer 4 provided with a conventional impact motor, not illustrated in more detail in the figures.
  • the front end of the percussive machine 4 receives the shank 1 as shown in FIG. 6 and embraces by means of an aside-swingable tool holder 5 a rear part of the shaft portion 3 in front of a circumferential collar 6 arranged between the shank l and the rear part of the shaft portion 3.
  • the shaft portion 3 transmits the impacts to the working section 2 and the tool is thereby set in noiseproducing vibrations.
  • the shaft portion 3 is provided with one or more vibration dampeners 7 of a novel type appearing in more detail in FIGS.
  • the vibration dampener 7 comprises a damping element in the form of a rubber or elastomeric cushion 8 which has a thickness preferably exceeding half the thickness of the shaft portion 3.
  • the rubber cushion 8 straddles the shaft portion 3 in saddle-like manner eccentrically and is clamped unilaterally thereagainst by means of a metallic sleeve 10 preferably of steel.
  • the sleeve 10 encases the rubber cushion 8 and has one or more, preferably two, longitudinal compressing ridges or loops ll, 12 which project in transverse outward direction of the tool for purposes of enabling clamping of the rubber cushion 8 unilaterally to the shaft portion 3 by shrinking together of the partly-cylindrical portions 13, 14 ofthe sleeve 10 which are located between the ridges 1-1, 12.
  • the compression of the ridges ll, 12 is carried out by bending the sleeve 10 along longitudinal lines at the base of the ridges with adouble pair of tong jaws by means of which the ridges 11 and 12 are simultaneously compressed thereby squeezing the portions l3, 14 towards each other with great power.
  • a thin frictional coating or liner (of plastic or rubber) with a thickness in the order of 0.5 mm, can be applied before clamping on or between the elements 14 and 3 as has been indicated by numeral 15 in FIG. 4.
  • the ridges ll, 12 project laterally relative to the tool, FIG. 5, and are disposed adjacent the interface between the damping element 8 and the shaft portion 3.
  • the compressing loops l1, l2 and the damping element 8 willnormally not encounter compact unbroken portions of the working material.
  • Unbroken working material will normally affeet the vibration dampener 7, FIG. 7, only at its strongest point,.i.e. the one where bending the frictional forces are transmitted via the side portion 14 of the sleeve 10 directly to the shaft portion 3.
  • the coating 15, FIG. 4, assists in such direct transmission and in preventing undesirable axial displacements of the vibration dampener 7.
  • vibration dampeners 7 can be utilized simultaneously on the shaft portion 3.
  • the number of damping elements 7 is chosen so that one obtains the most efficient silencing with respect to the working conditions of the tool.
  • the operational conditions and the type of tool and hammer to be used are decisive for how big a part of the shaft portion that on the whole can be used for the disposition of vibration dampeners.
  • the silencing effect as such is determined by the fact that the tool like a tuning fork is being silenced by the vibration dampener suppressing the vibrations thereof.
  • the damping element 7 again comprises of a rubber or elastomeric cushion 8 which in saddle-like manner is kept in place by a modified protecting and encasing sleeve 20.
  • the latter is a metallic sleeve, preferably of steel, with cylindrical initial shape.
  • the sleeve 20 has an internal perimeter somewhat larger. than the perimeter of the collar 6. While in cylindricalstate, the sleeve 20 is moved over the collar 6, notshown, FIGS 7-9 but appearing in .FIGS. 1, 2 and 6, and is thereupon squeezed to oval shape.
  • the liner 1? comprises of friction material of brake lining type, for example incorporatingasbestos fibres in rubber as a carrying material and may have a thickness of at most 2 mm. It should have a hardness of about 90IR H and such floatability under compression that the surface irregularities in the shaft portion 3 and the sleeve 20 are filled out during final setting of the sleeve 20. f g
  • the rubber cushion 8 preferably is comprised of silicone rubber with a hardness in the order of IRH. Silicone rubber has good vibration damping properties and high resistance to heat. The heat resistance is im portant in the present application because of the damping element generating heat in the course of damping.
  • the rubber cushion 8 is preferably glued by a'suitable adhesive in place against the shaft portion 3 arid the inner surface of the sleeve 20.
  • the liner 17 may be coated with adhesive, as well, for instance by phenolic resin glue.
  • the sleeve 20 is shrunk radially and there is attained a strong attachment of the components 8, l7 and 20 to the shaft portion 30.
  • adhesive prior :to bending the binding together of theinvolved components is further. promoted. i
  • the ridge 18 protrudin'g i'nto rubber cushion 8 eliminates the need oflateral compression ridges ll, 12 for the vibration dampener 7 shown in FIGS. 4 and 5, whereby a more compact and stronger embodiment is attained.
  • the openings 21 between the rubber cushion 8 and the liner 1? promote cooling by ventilation.
  • Silencing can be attained with fairly good results also in the simplified embodiment illustrated in FIG. 10 in which the cushion 8 of suitable rubber, for example natural or silicone rubber, isvulcanized fast to the shaft portion 3 along the material portion designated by nu meral 22.
  • the shaft portion'3 may be provided with one or possibly several upwardly forged ribs 23.
  • the clamping sleeve for the rubber cushion 8 is dispensed with, the rubber cushion 8 then, however, receiving less protection during work.
  • a method according to claim 1 further comprising clamping a retaining liner between said sleeve and said shaft portion in opposite position to said eccentric mass portion of said vibration damping element.
  • a method according to claim 1 further comprising locally bending said sleeve adjacent an interface between said vibration damping element and said shaft portion.
  • a method according to claim 1 further comprising locally bending said sleeve by forming at least-one longitudinal ridge along its full length and depressed into said eccentric mass portion of said vibration damping element.
  • vibration damping element straddles in'a saddle-like manner substantially only one circumferential side of said shaft portion and comprising locating a retaining liner between said shaft portion and the portion of said sleeve opposite to said vibration damping element.
  • a silenced percussion tool comprising:
  • vibration dampener on said shaft portion and axially spaced from said collar, said vibration dampener including a vibration damping element comprising a large mass portion extending substantially over the whole length thereof which large mass portion straddles in saddle-like manner only a portion of the circumference of said shaft portion for silencing'said noise; and I means extending axially of said shaft portion an being substantially coextensive with saidvibration damping element in the axial direction of said shaft portion for affixing said vibration damping element to said tool in simultaneous unilateral surface contact and with said large mass portion in eccentric mass relation thereto.
  • said affixing means includes at least one sleeve encasing said vibration damping element and circumferentially clamping said vibration element to said shaft portion;
  • a silenced tool in which said sleeve has at least one longitudinal inwardly directed ridge along its full length and depressed into said large mass portion of said vibration damping element for clamping said sleeve therearound and around said shaft 1 vibration damping element and shaft portion.
  • a silenced percussion tool comprising;
  • vibration dampener on said shaft portion and axially spaeed from said collar, said vibration dampener including a vibration damping element comprising a large mass portion which in saddle-like manner eccentrically straddles a portion of the circumference of said shaft portion for silencing said noise;
  • At least one undivided metallic sleeve having an internal perimeter larger than the perimeter of said collar and for circumferentially clamping said vibration damping element to said shaft portion for affixing said vibration damping element to said tool in unilateral surface contact therewith, and with said vibration damping element confined to substantially one side of said shaft portion;
  • a silenced tool according to claim 13 in which said sleeve has at least one longitudinal inwardly directed ridge along its full length and depressed into said large mass portion of said vibration damping element for clamping said sleeve therearound and around said shaft portion.
  • a retaining collar adjacent said shank I a working section; r v a shaft portion disposed between said collar and said I prising a large mass portion which in saddle-like manner straddles substantially only one circumferential side of said shaft portion for silencing said noise; and

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Braking Arrangements (AREA)
  • Portable Nailing Machines And Staplers (AREA)
US416232A 1972-11-22 1973-11-15 Eccentric element for silencing tool and method Expired - Lifetime US3918530A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
SE7215224A SE371770B (fr) 1972-11-22 1972-11-22

Publications (1)

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US3918530A true US3918530A (en) 1975-11-11

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US416232A Expired - Lifetime US3918530A (en) 1972-11-22 1973-11-15 Eccentric element for silencing tool and method

Country Status (9)

Country Link
US (1) US3918530A (fr)
AT (1) AT341455B (fr)
CA (1) CA998895A (fr)
CH (1) CH572381A5 (fr)
DE (1) DE2357306C3 (fr)
FR (1) FR2207786B1 (fr)
GB (1) GB1398693A (fr)
SE (1) SE371770B (fr)
ZA (1) ZA738721B (fr)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4168754A (en) * 1976-05-07 1979-09-25 Nyholm Bengt V Impact tool
US4191273A (en) * 1978-06-05 1980-03-04 Allis-Chalmers Corporation Seal and sound attenuator for control console
US4615359A (en) * 1982-08-30 1986-10-07 Affa Stephen N Shroud for aircraft duct
US4691741A (en) * 1983-06-01 1987-09-08 General Connectors Corporation Shroud for aircraft duct
US4693339A (en) * 1986-10-16 1987-09-15 Newport News Shipbuilding And Dry Dock Company Muffler for gas inducting machinery generating low frequency noise
US4699243A (en) * 1985-01-28 1987-10-13 Honda Giken Kogyo Kabushiki Kaisha Vibration isolating pipe
US4706788A (en) * 1985-04-15 1987-11-17 Melles Griot, Irvine Company Vibration damped apparatus
US4723926A (en) * 1985-05-14 1988-02-09 Sanshin Kogyo Kabushiki Kaisha Non-vibrating structure of an outboard motor
US5244521A (en) * 1991-05-31 1993-09-14 Ligman Gary A Pneumatic tool muffler system
US20030026669A1 (en) * 2001-07-06 2003-02-06 Marco Lang Chisel
US20070024013A1 (en) * 2005-07-28 2007-02-01 Udo Hauptmann Chuck
US20080066939A1 (en) * 2005-06-08 2008-03-20 Manacorda Thiago P Kits and methods to provide anti-vibration protection to hand-held impact tools
CN101743098A (zh) * 2007-07-13 2010-06-16 长年Tm公司 用于气动工具的噪声抑制装置
US20110049817A1 (en) * 2009-08-26 2011-03-03 Hilti Aktiengesellschaft Tool holder

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2851160A1 (de) * 1978-11-25 1980-06-04 Wacker Werke Kg Vorrichtung zum mindern der geraeuschentwicklung an den werkzeugen von bohr- und aufbruchhaemmern
DE19544482C2 (de) * 1995-11-29 1998-03-12 Hans Eichner Gmbh & Co Kg Verfahren und Werkzeug zum Entschichten mit Brennstoffrückständen beschichteter Rohre der Heizflächen einer Kesselfeuerung

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2889811A (en) * 1956-08-10 1959-06-09 Electro Chimie Metal Percussion tools
US3263770A (en) * 1964-10-19 1966-08-02 Atlas Copco Ab Noise deadening means for percussive tools
US3662855A (en) * 1970-05-04 1972-05-16 Robert D Adams Muffled tool for vibratory or impact machines
US3783970A (en) * 1972-06-07 1974-01-08 Thor Power Tool Co Sound attenuating device for a work steel or the like
US3848931A (en) * 1972-10-10 1974-11-19 Int Tool Sales Tool bit for vibration attenuation

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2889811A (en) * 1956-08-10 1959-06-09 Electro Chimie Metal Percussion tools
US3263770A (en) * 1964-10-19 1966-08-02 Atlas Copco Ab Noise deadening means for percussive tools
US3662855A (en) * 1970-05-04 1972-05-16 Robert D Adams Muffled tool for vibratory or impact machines
US3783970A (en) * 1972-06-07 1974-01-08 Thor Power Tool Co Sound attenuating device for a work steel or the like
US3848931A (en) * 1972-10-10 1974-11-19 Int Tool Sales Tool bit for vibration attenuation

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4168754A (en) * 1976-05-07 1979-09-25 Nyholm Bengt V Impact tool
US4191273A (en) * 1978-06-05 1980-03-04 Allis-Chalmers Corporation Seal and sound attenuator for control console
US4615359A (en) * 1982-08-30 1986-10-07 Affa Stephen N Shroud for aircraft duct
US4691741A (en) * 1983-06-01 1987-09-08 General Connectors Corporation Shroud for aircraft duct
US4699243A (en) * 1985-01-28 1987-10-13 Honda Giken Kogyo Kabushiki Kaisha Vibration isolating pipe
US4706788A (en) * 1985-04-15 1987-11-17 Melles Griot, Irvine Company Vibration damped apparatus
US4723926A (en) * 1985-05-14 1988-02-09 Sanshin Kogyo Kabushiki Kaisha Non-vibrating structure of an outboard motor
US4693339A (en) * 1986-10-16 1987-09-15 Newport News Shipbuilding And Dry Dock Company Muffler for gas inducting machinery generating low frequency noise
US5244521A (en) * 1991-05-31 1993-09-14 Ligman Gary A Pneumatic tool muffler system
US20030026669A1 (en) * 2001-07-06 2003-02-06 Marco Lang Chisel
US8215415B2 (en) * 2001-07-06 2012-07-10 Hawera Probst Gmbh Chisel
US20080066939A1 (en) * 2005-06-08 2008-03-20 Manacorda Thiago P Kits and methods to provide anti-vibration protection to hand-held impact tools
US7703547B2 (en) * 2005-06-08 2010-04-27 EMBRAER—Empresa Brasileira de Aeronautica S.A. Hand-held impact tools having anti-vibration protection
US20070024013A1 (en) * 2005-07-28 2007-02-01 Udo Hauptmann Chuck
CN101743098A (zh) * 2007-07-13 2010-06-16 长年Tm公司 用于气动工具的噪声抑制装置
US20110049817A1 (en) * 2009-08-26 2011-03-03 Hilti Aktiengesellschaft Tool holder

Also Published As

Publication number Publication date
DE2357306B2 (de) 1974-12-05
SE371770B (fr) 1974-12-02
FR2207786A1 (fr) 1974-06-21
AU6263373A (en) 1975-05-22
FR2207786B1 (fr) 1977-03-11
AT341455B (de) 1978-02-10
DE2357306A1 (de) 1974-06-06
ZA738721B (en) 1974-10-30
DE2357306C3 (de) 1975-07-10
CH572381A5 (fr) 1976-02-13
ATA976473A (de) 1977-05-15
CA998895A (en) 1976-10-26
GB1398693A (en) 1975-06-25

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