EP0065142A2 - Outil d'enfoncement d'éléments de fixation amortisseur de son - Google Patents

Outil d'enfoncement d'éléments de fixation amortisseur de son Download PDF

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Publication number
EP0065142A2
EP0065142A2 EP82103618A EP82103618A EP0065142A2 EP 0065142 A2 EP0065142 A2 EP 0065142A2 EP 82103618 A EP82103618 A EP 82103618A EP 82103618 A EP82103618 A EP 82103618A EP 0065142 A2 EP0065142 A2 EP 0065142A2
Authority
EP
European Patent Office
Prior art keywords
valve member
driving tool
main valve
tool according
driving
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.)
Withdrawn
Application number
EP82103618A
Other languages
German (de)
English (en)
Other versions
EP0065142A3 (fr
Inventor
Wolfgang Elliesen
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.)
Joh Friedrich Behrens AG
Original Assignee
Joh Friedrich Behrens AG
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 Joh Friedrich Behrens AG filed Critical Joh Friedrich Behrens AG
Publication of EP0065142A2 publication Critical patent/EP0065142A2/fr
Publication of EP0065142A3 publication Critical patent/EP0065142A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25C—HAND-HELD NAILING OR STAPLING TOOLS; MANUALLY OPERATED PORTABLE STAPLING TOOLS
    • B25C1/00—Hand-held nailing tools; Nail feeding devices
    • B25C1/04—Hand-held nailing tools; Nail feeding devices operated by fluid pressure, e.g. by air pressure
    • B25C1/047—Mechanical details
    • 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

Definitions

  • the invention relates to a soundproofed driving tool for fasteners, -in which the valve member of the main valve is arranged above a working cylinder and in the upper position separates the working cylinder from a compressed air source and connects it to the atmosphere, and in the lower position connects the working cylinder to the compressed air source and blocks the connection with atmosphere, and in which the space above the main valve member can be connected alternately with atmosphere or compressed air and in which a sound-absorbing means is arranged in the room above the main valve member.
  • Compressed air powered driving tools are used to process fasteners such as staples, nails, pins, screws, etc.
  • a complete working cycle of such driving tools consists of a driving in and a blowing out phase.
  • the piston is pressurized with compressed air and accelerated so that the fastener is driven in at high speed on the stroke.
  • the excess residual energy of the piston which is not used during the driving process, is collected at the end of the stroke by a buffer element.
  • the working piston returns to its starting position and thereby pushes the air in the working cylinder into the atmosphere.
  • Both work cycles cause impulsive air and structure-borne noise of different intensities.
  • the level-determining airborne noise emitted in the driving-in phase is created by the piston striking the end of the stroke on the buffer element.
  • high-frequency noises are caused by the compressed air flowing out.
  • the invention has for its object to provide a soundproofed driving tool for fasteners that provides effective means for sound and vibration damping for the driving phase.
  • a delay disk above the main valve member is axially movably supported and a resilient damping material is arranged between the delay disk and the facing housing wall.
  • a relatively small, meanwhile movable mass is used to achieve an equal or better effect.
  • the direction of movement of the deceleration disk is opposite to that of the main valve member. This is based on the fact that the space above the valve member is alternately placed in compressed air or atmosphere. To initiate the opening process, this space is vented to the atmosphere so that the valve member lifts off the cylinder and moves in the direction of the device housing cap.
  • the delay disk which in turn rests against the resilient damping material, is moved by the latter in the direction of the valve member, as a result of which the movement of the valve member is more or less braked and both parts, namely valve member and delay disk, continue the original travel of the valve member until the delay disk is under again Deformation of the damping material against this applies firmly.
  • the valve member can be braked over a longer period of time, and shock-like impacts are also mitigated in that the retarding disk on the one hand and the valve member on the other hand are formed from different materials.
  • the main valve member is therefore preferably formed from a relatively light material, preferably plastic, according to an embodiment of the invention, while the delay disk is formed from a relatively heavy material, preferably brass.
  • the individual components can also be dimensioned so that the actual Braking process of the main valve member takes place at a time when the piston hits the lower buffer element to be provided anyway. Since this shock is far stronger than the recoil caused by the valve member, the recoil can thus be completely compensated for.
  • an 0-ring is arranged between the retardation disk and the housing wall.
  • the 0-ring serves on the one hand as a noise-damping stop for the retarding disk and on the other hand as spring means which prestresses the retarding disk in the direction of the main valve member.
  • the O-ring can be arranged both in the retardation disk and in the housing itself, preferably a further embodiment of the invention provides that the O-ring sits in a groove in the housing wall.
  • knobs or similar elevations are arranged on the upper side of the main valve member. It is understood that such elevations can also be formed in the retardation disk. There is also the possibility of accommodating such knobs as separate parts, for example made of an elastomeric material, in recesses in the delay disk or the valve member.
  • a further embodiment of the invention provides that a first section and a second section of the buffer element are shaped such that they are successively deformed when the driving piston strikes.
  • the following considerations have been taken as a basis here: Only a relatively small distance is available for braking the driving piston at the end of the stroke. Therefore, it makes little sense to make the buffer element relatively soft in order to avoid hard impacts. After performing relatively small deformation work, the driving plunger comes to a "stop", which in turn creates a shock or impact. On the other hand, as I said, a relatively hard material for braking purposes leads to relatively hard impacts.
  • the invention now provides two different sections on the buffer element, against which the driving piston abuts one after the other at the stroke end. If the residual energy at the end of the stroke is relatively small, only the first section with which the driving piston comes into contact needs to perform braking work. If the residual energy is greater, for example in the case of a free shot, the second section for braking the driving piston also comes into play. Only a driving piston which is braked by deformation work over the entire range of the remaining energy causes no blows or a shock-like interception, as is known Lich very high vibration amplitudes are caused. In a further embodiment of this, the invention provides that the inner and outer sections are formed by two radially spaced, coaxially extending beads.
  • the driving piston preferably first comes into contact with the inner bead and deforms it radially. With greater residual energy, the outer bead is then compressed more or less axially. With such a design of the damping element, the temporal expansion of the braking process can be carried out sufficiently to optimize damping.
  • two radially spaced coaxially extending beads are also formed on the underside of the one-piece shaped buffer element and the inner bead cooperates with the conical outer surface of a guide member known per se.
  • the guide member serves for the safe guidance of the driving plunger attached to the driving piston.
  • the guide member is advantageously provided with a conical outer surface, so that the inner bead is radially expanded when the entire damping ring moves downward and contributes to effective braking.
  • an embodiment of the invention provides that at least one, preferably a plurality of ribs spaced apart in the circumferential direction are arranged on the outside of the buffer element, said ribs abutting the wall of the working cylinder. Via the gap formed by the ribs, the air can escape from the above-mentioned annular space below the buffer element. This air is heated to a relatively high degree, since the damping element experiences an extremely strong heating due to the internal friction of the material. If the buffer element relaxes again when the driving piston returns and moves upward, thereby enlarging the annular space mentioned, cooler air can sweep past the damping element into the lower annular space and thereby cool the damping element.
  • an embodiment of the invention provides that an insulating member made of heavy or yielding material is arranged on the cylinder bottom below the buffer element.
  • the insulating member is preferably formed on the underside with ribs or similar projections; so that the transmission surface for structure-borne noise reaches only a small dimension.
  • the driving tool shown in FIG. 1 contains a handle housing 10, a cylinder housing 11, a magazine 12 for fastening means and a mouth tool 13 with a not shown firing channel for a driving plunger 14 which is fastened to a driving piston 15.
  • the driving piston 15 is guided by a working cylinder 16, which is known in the art L äuse manner in Zylindergel is attached. 11 This and the required sealing are not dealt with.
  • a compressed air reservoir 17 is located in the handle housing 10.
  • a trigger valve 18 is also arranged in the handle housing, the valve slide 19 of which is actuated in a known manner with the aid of a trigger lever 20.
  • a control valve 21 is arranged in the handle housing 10, which contains an axially movable valve slide 22. Where necessary, further details are discussed in connection with the description of the function of the device described.
  • the top of the cylinder housing 11 or the cylinder 16 is closed by a cap 23 which is attached to the cylinder housing 11 in a known manner.
  • the cap 23, which in turn is open at the top, is closed off by a plate 24 which receives a bush-like valve seat element 25 in an axial collar or in its blind bore.
  • the valve seat element 25 interacts with a pierced axial collar 26 of a main valve member 27, which is movably and sealingly mounted in a bore 28 of the cap 23. In the rest position, the valve member 27 lies against the end face of the cylinder 16.
  • valve member 27 there is a delay disk 29 in the bore 28.
  • the delay disk 29 is preferably made of one heavier material, for example brass. It has a central through-hole through which the axial collar 26 of the valve member 27 is guided in a sealing manner (0-ring). Between the valve member 27 and the delay disk 29, a conical spring 30 is arranged, which tries to push the two parts apart.
  • an O-ring 31 is attached in a groove, which partially projects into the bore 28 in the relaxed state (see also FIG. 2).
  • the through bore 32 of the valve member 27 is connected to the atmosphere via a first chamber 33 in the cap 23 and a second chamber 34 connected to it and a channel 35 and a silencer 36.
  • the cylinder housing 11 and the cylinder 16 are closed at the lower end by a cap 38.
  • an insulating member 39 is supported from relatively heavy plastic material. It has toothed ribs 40 in cross section, by means of which it is supported on the bottom cap 38.
  • a guide member 41 which contains a central bore for guiding the driving plunger 14 and on the outside a downwardly diverging conical surface 42.
  • a buffer ring 43 is arranged, which is constructed symmetrically to a transverse axis .
  • Valve slide 22 moves upwards into the position shown in FIG. 2, thereby venting space 48 through an opening 50 in housing cap 23.
  • the pressure acting from below against the valve member 27 moves the valve member 27 upward against the pressure of the spring 30.
  • the decelerating disk 29 moves downward under the pressure of the 0-ring.31, so that on a medium distance both parts move against each other bump.
  • the shock is dampened by knobs 51 on the top of the valve member 27.
  • the unit consisting of the retarding disk 29 and the valve member 27 then moves upwards until the axial collar 26 abuts against the valve seat element 25 or the retarding disk 29 against the 0-ring 31. This ends the movement of these parts.
  • the air from the reservoir 17 now fully acts on the piston 15 and drives it down in a known manner in order to drive a fastener into a workpiece.
  • Fig. 3 the interception of the driving piston 15 is shown at the end of the stroke.
  • the piston has a conical surface 52, which moves into the opening of the buffer ring 43 at the lower end and thus progressively deforms the inner bead 44 radially outward.
  • an axial force is exerted on the buffer ring 43.
  • the buffer ring 43 moves downward, the lower inner bead 44 also being progressively deformed radially outward as it runs along the conical surface 42.
  • This deformation work it is normally sufficient to destroy the residual energy which remains in the piston 15 when the fastener is knocked in.
  • the outer section of the piston 15 strikes the outer bead 45 from above, so that the lower and upper outer beads are axially more or less compressed. This effectively consumes the remaining part of the residual energy.
  • the piston 15 During its downward movement, the piston 15 has pressed part of the air it has pushed in front of it via openings 53 into an annular space 54.
  • An O-ring 55 ensures in a known manner that the air from the annular space 54 cannot flow back into the cylinder 16.
  • the annular space formed by the cylinder housing 11 and cylinder 16 is also connected via openings 56 to the space below the piston 15 in its end position. The piston 15 is acted upon from the underside via these openings 56 in order to be moved back into the upper end position.
  • the annular space 57 located underneath it is inevitably reduced.
  • the gap formed by the webs 47 enables the air to flow upward from the annular space 57 and to escape into the annular space 54 through the opening.
  • the insulating member 39 contributes to the fact that impulse-like noises that are still present are not emitted to the outside via the base cap 38.
  • the piston 15 presses the air above it through the through hole 32 and the chambers 33, 34, the channel 35 and the silencer 36 to the outside. If the trigger lever 20 and thus the trigger valve 18 are not actuated, take it. the valves 18 and 21 again the position shown in Fig. 1. As a result, the main valve member 27 can close and establish the aforementioned connection of the cylinder space to the atmosphere. This completes an entire work cycle.
  • the structure of the magazine 12, which is shown in more detail in FIG. 5, is not to be discussed in detail. It should only be mentioned that the magazine 12 shown is shaped for headed nails, which nails are combined into a magazine strip with the aid of plastic webs. From Fig. 5 it can also be seen that a layer 60 of structure-borne sound absorbing material is attached to the handle housing. Layers 60 of this type can be applied at several points, above all on surfaces that emit a lot of sound, and at the same time serve as a gentle storage surface for the device housing.

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  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Portable Nailing Machines And Staplers (AREA)
EP82103618A 1981-05-20 1982-04-28 Outil d'enfoncement d'éléments de fixation amortisseur de son Withdrawn EP0065142A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3119956 1981-05-20
DE3119956A DE3119956C2 (de) 1981-05-20 1981-05-20 Schallgedämpftes Eintreibgerät für Befestigungsmittel

Publications (2)

Publication Number Publication Date
EP0065142A2 true EP0065142A2 (fr) 1982-11-24
EP0065142A3 EP0065142A3 (fr) 1983-11-30

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP82103618A Withdrawn EP0065142A3 (fr) 1981-05-20 1982-04-28 Outil d'enfoncement d'éléments de fixation amortisseur de son

Country Status (4)

Country Link
US (2) US4509669A (fr)
EP (1) EP0065142A3 (fr)
JP (1) JPS57201182A (fr)
DE (1) DE3119956C2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0661140A1 (fr) * 1993-12-03 1995-07-05 Kanematsu-Nnk Corporation Outil d'enfoncement d'attaches
GB2294657A (en) * 1994-11-07 1996-05-08 Max Co Ltd Silencer for pneumatic machines
EP0720892A1 (fr) * 1995-01-04 1996-07-10 Joh. Friedrich Behrens AG Outil d'enforcement des moyens de fixation

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DE3308630C2 (de) * 1983-03-11 1994-10-27 Signode Corp Nagelmagazinierungseinheit
DK133284A (da) * 1983-03-11 1984-09-12 Signode Corp Soeminddrivningsapparat og soemmagasineringsenhed
EP0205633B1 (fr) * 1985-06-21 1988-01-27 Joh. Friedrich Behrens AG Assemblage de soupape
DE3730048A1 (de) * 1987-09-08 1989-03-16 Bosch Gmbh Robert Handwerkzeugmaschine
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US6321853B2 (en) 1999-10-01 2001-11-27 Chicago Pneumtic Tool Company Vibration isolated impact wrench
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US7165305B2 (en) * 2004-04-02 2007-01-23 Black & Decker Inc. Activation arm assembly method
US7322506B2 (en) * 2004-04-02 2008-01-29 Black & Decker Inc. Electric driving tool with driver propelled by flywheel inertia
US7331403B2 (en) * 2004-04-02 2008-02-19 Black & Decker Inc. Lock-out for activation arm mechanism in a power tool
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US7138595B2 (en) 2004-04-02 2006-11-21 Black & Decker Inc. Trigger configuration for a power tool
ATE531484T1 (de) * 2004-04-02 2011-11-15 Black & Decker Inc Treiberkonfiguration für ein kraftbetriebenes werkzeug
US8123099B2 (en) * 2004-04-02 2012-02-28 Black & Decker Inc. Cam and clutch configuration for a power tool
US7503401B2 (en) * 2004-04-02 2009-03-17 Black & Decker Inc. Solenoid positioning methodology
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DE102005000113B4 (de) * 2005-09-13 2014-03-27 Hilti Aktiengesellschaft Setzgerät
DE102005000114A1 (de) * 2005-09-13 2007-03-15 Hilti Ag Setzgerät
US20070152013A1 (en) * 2006-01-05 2007-07-05 Hao Cheng Technology Corp. Nail gun back cover
US8342303B2 (en) * 2006-07-28 2013-01-01 Hitachi, Ltd. Valve apparatus
US7556184B2 (en) * 2007-06-11 2009-07-07 Black & Decker Inc. Profile lifter for a nailer
DE102007000391A1 (de) * 2007-07-19 2009-01-22 Hilti Aktiengesellschaft Handwerkzeugmaschine mit Schlagwerk
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US7690546B2 (en) * 2007-08-31 2010-04-06 Illinois Tool Works Inc. Pneumatic tool actuation device
US7982580B2 (en) * 2008-05-30 2011-07-19 Rosemount Inc. High vibration thin film RTD sensor
US7975777B2 (en) 2008-12-19 2011-07-12 Robert Bosch Gmbh Cellular foam bumper for nailer
US8387846B2 (en) 2009-06-08 2013-03-05 Illinois Tool Works Inc Fastening tool with blind guide work contact tip
TWI387514B (zh) * 2010-09-20 2013-03-01 Basso Ind Corp High pressure nail gun that eliminates exhaust noise
DE102010044011A1 (de) * 2010-11-16 2012-05-16 Hilti Aktiengesellschaft Handwerkzeugmaschine
US8708061B2 (en) 2010-12-14 2014-04-29 Caterpillar Inc. Lower damper for demolition hammer
CN203092484U (zh) * 2013-02-22 2013-07-31 郭景辉 一种用于射钉枪的卸力装置
US10717179B2 (en) * 2014-07-28 2020-07-21 Black & Decker Inc. Sound damping for power tools
JP6492280B2 (ja) * 2015-12-08 2019-04-03 株式会社丸高工業 エアータッカー

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0661140A1 (fr) * 1993-12-03 1995-07-05 Kanematsu-Nnk Corporation Outil d'enfoncement d'attaches
GB2294657A (en) * 1994-11-07 1996-05-08 Max Co Ltd Silencer for pneumatic machines
US5676300A (en) * 1994-11-07 1997-10-14 Max Co., Ltd. Sound reduction apparatus for pneumatic type nailing machine
GB2294657B (en) * 1994-11-07 1997-12-10 Max Co Ltd Sound reducer for pneumatic machines
EP0720892A1 (fr) * 1995-01-04 1996-07-10 Joh. Friedrich Behrens AG Outil d'enforcement des moyens de fixation

Also Published As

Publication number Publication date
EP0065142A3 (fr) 1983-11-30
JPS6250274B2 (fr) 1987-10-23
DE3119956A1 (de) 1982-12-23
US4509669A (en) 1985-04-09
US4609135A (en) 1986-09-02
DE3119956C2 (de) 1984-11-22
JPS57201182A (en) 1982-12-09

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