EP0274957A1 - Setzgerät mit Treibkolben - Google Patents

Setzgerät mit Treibkolben Download PDF

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Publication number
EP0274957A1
EP0274957A1 EP87402935A EP87402935A EP0274957A1 EP 0274957 A1 EP0274957 A1 EP 0274957A1 EP 87402935 A EP87402935 A EP 87402935A EP 87402935 A EP87402935 A EP 87402935A EP 0274957 A1 EP0274957 A1 EP 0274957A1
Authority
EP
European Patent Office
Prior art keywords
ring
piston
rigid
elastic
guide
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.)
Granted
Application number
EP87402935A
Other languages
English (en)
French (fr)
Other versions
EP0274957B1 (de
Inventor
Roland Almeras
Jean-Claude Vernerey
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.)
Societe de Prospection et dInventions Techniques SPIT SAS
Original Assignee
Societe de Prospection et dInventions Techniques SPIT SAS
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 Societe de Prospection et dInventions Techniques SPIT SAS filed Critical Societe de Prospection et dInventions Techniques SPIT SAS
Publication of EP0274957A1 publication Critical patent/EP0274957A1/de
Application granted granted Critical
Publication of EP0274957B1 publication Critical patent/EP0274957B1/de
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
    • B25C—HAND-HELD NAILING OR STAPLING TOOLS; MANUALLY OPERATED PORTABLE STAPLING TOOLS
    • B25C1/00—Hand-held nailing tools; Nail feeding devices
    • B25C1/08—Hand-held nailing tools; Nail feeding devices operated by combustion pressure
    • B25C1/10—Hand-held nailing tools; Nail feeding devices operated by combustion pressure generated by detonation of a cartridge
    • B25C1/14—Hand-held nailing tools; Nail feeding devices operated by combustion pressure generated by detonation of a cartridge acting on an intermediate plunger or anvil

Definitions

  • the present invention relates to an indirect fire sealing apparatus, comprising a piston mounted in a barrel for, under the action of the combustion gases of a propellant charge, driving a pad for fixing a part on a support, means piston damping being provided between the barrel and a buffer guide disposed in front of the barrel, to absorb the excess propulsion energy of the piston and limit its stroke, the damping means comprising in combination, a ring, shaped to cooperate with the piston head, a first intermediate ring, of elastic material, disposed between the cooperation ring with the piston head and the buffer guide, and a second intermediate ring, of rigid but slightly deformable material, displaceable axially between the cooperation ring with the piston head and the buffer guide.
  • Sealing devices of this type are often used for cladding buildings, such as hangars. It is, for example, and using short buffers, to fix cladding sheets on section beams, for example in I.
  • the thicknesses of the support materials for receiving the fixing buffers are variable from one material to another, and it is necessary to ensure the regularity of the insertion of the pads in these materials.
  • I-beams to be covered with thin sheets, it often happens that operators work blindly, without knowing if they are pulling in the soul of the beams, in their thin side wings, or even next to it.
  • the buffers could be too deep, which would be detrimental to the quality of the fixing, but if it is next to it, they could cross the thin sheets like a real projectile animated with a still high speed, if the sealing device was precisely not provided with the damping means of the piston which limit its stroke, not to mention the devices which are based on the absorption of the excess power by the depression of the buffer itself, and in which the piston may protrude out of the stamp guide.
  • the damper of the piston is therefore intended to limit, or control, the stroke. Indeed, it is sufficient to ensure the position of the piston at the moment when, so to speak, it releases the tampon, because at this moment, the kinetic energy of the tampon represents only a very small portion of the energy propulsion, insufficient for it to continue its driving course. In other words, as soon as the tampon is released by the piston, it stops.
  • shock absorber Several types are already known, non-elastic steel rings, on the one hand, and rings made of elastic material, for example polyurethane, on the other hand.
  • Steel rings offer the advantage of good driving precision, but they have the disadvantage of increasing the risk of the piston breaking by sudden stop.
  • the elastic rings do not have this drawback. But due to the fact that they are stressed in a large and frequent manner, they deform and even fall apart to the detriment of the precision of positioning of the piston and of the functioning of the tool.
  • the present invention therefore aims to provide an indirect firing sealing apparatus, in which the axial position of the piston, after firing, is always the same.
  • the present invention relates to an indirect firing sealing apparatus of the type mentioned above, characterized in that the buffer guide and the second rigid intermediate ring are arranged so that the length of the axial displacement of the latter is equal to the decrease in the axial dimension of the elastic intermediate ring after compression.
  • the ring of cooperation with the piston head can start to absorb a certain part of the propulsion energy, by shrinking, before moving forward and compressing the first elastic intermediate ring between it and the tip guide, without risk of causing the piston to break.
  • the first elastic intermediate ring first serves to limit the forward movement of the cooperation ring with the piston head.
  • This first elastic intermediate ring also behaves like a compression spring with turns.
  • the second rigid intermediate ring coming to bear against the buffer guide, provides a stop function to prevent this so-called spring from coming into contiguous turns.
  • the rigid intermediate ring makes it possible to control the deformation of the elastic intermediate ring and prevents the latter from being disintegrated by excessive crushing.
  • the rigid intermediate ring collects the excess energy which has not already been absorbed by the elastic intermediate ring.
  • the rigid intermediate ring but slightly deformable, protects the elastic ring which can thus regain all its characteristics, even after numerous dampings of the piston, which is beneficial to the precision of the positioning of the piston.
  • the buffer guide comprises a rear recess for receiving the second rigid intermediate ring of axial depth at least equal to the reduction in the axial dimension of the elastic intermediate ring after compression.
  • the axial dimension of the two intermediate rings is the same.
  • the association of two rings of the same axial dimension has the advantage of a simplification of assembly, by not being obliged to respect a positioning and a direction of assembly.
  • the two rings represent an inseparable damping assembly which is easily interchangeable, and which can give all the guarantees of positioning of the piston, when the latter reaches the end of the stroke, and which therefore makes it possible to always obtain a quality fixing.
  • the cooperation ring with the piston head is made of rigid material.
  • an annular space is provided around the two intermediate rings to allow, under the action of the displacement of the cooperation ring with the piston head, the swelling of the first intermediate ring in elastic material, until the second intermediate ring of rigid and deformable material abuts against the rear bottom of the tip guide.
  • the length of the axial displacement of the rigid intermediate ring and the volume of the space surrounding the two intermediate rings can be such that, at the end of the deformation phase of the elastic intermediate ring, when the rigid intermediate ring abuts against the rear bottom of the tip guide, said volume is not zero.
  • the piston head is hollowed out to receive the load carrier, whereby the robustness of the piston remains preserved despite the reduction in its weight which, for its part, is conducive to its good damping.
  • the sum of the axial lengths of the elastic intermediate ring, in its compressed state, and of the buffer guide, on the one hand, as well as the length of the front part of the piston intended to protrude from the elastic intermediate ring, on the other hand, are such that the front end of the piston, after firing, does not protrude out of the buffer guide.
  • the piston head of the apparatus of the invention is frustoconical, therefore of large surface area, and the ring for cooperation with the piston head has a bore of corresponding shape, which offers the best solution to the problem. of the depreciation applied.
  • the sealing device which will be described is used above all to fix parts 1, such as cladding sheets, on supports 2, such as hangar beams, using buffers which are advantageously in the form of nails with short rods. 3 and big-headed 4.
  • the apparatus of the invention therefore comprises a barrel block 5, in fact a barrel 51 proper and a load carrier 52 integral with the barrel, in which is mounted, for sliding axially, a piston, or counterweight, 6, and a buffer guide 7.
  • a shoulder spacer 8, integral with the buffer guide 7, comprises, at the rear, an internal annular rim 9 intended to cooperate with an external annular rim 10 which is provided, at the front, with the barrel 51 , so that, when opening the device after a shot and before loading a new propellant charge, the drive of the buffer guide 7 forwards drives with it the barrel block 5, while allowing , at the time of the firing and under the action of the exhaust gases, the retraction of the barrel 51 until its front edge 10 comes into abutment against the rear edge 9 of the spacer 8.
  • the piston 6 comprises a head 11 and a rod 12.
  • the head 11 comprises an annular rear part 13, hollowed out to receive, in the closed position of the apparatus and therefore ready for firing, the load carrier 52, and a front part 14 frustoconical, flared towards the rear, having a relatively large surface 15.
  • the rear of the piston head 11 has an external flange 16, by which the piston 6 slides in the barrel 5, and which is intended to cooperate with a retaining pawl 17 secured to the barrel holder, not shown, in which the barrel is slidably mounted, the pawl 17 being able to slide in a slot 53 formed in the barrel.
  • a retaining pawl 17 secured to the barrel holder, not shown, in which the barrel is slidably mounted, the pawl 17 being able to slide in a slot 53 formed in the barrel.
  • the load carrier 52 the front part of which is therefore intended to engage in the rear recess of the piston and in which a nozzle 19 for the propulsion gases is formed, comprises a rear part intended to receive, in a combustion chamber, a propellant charge 20 intended to be struck by a striker carried by the cylinder head of the device.
  • An internal frustoconical bore 23 is formed in the ring 22, of shape complementary to that of the front part 14 of the piston head.
  • a second intermediate ring 27 also in the form of a sleeve and of rigid but slightly deformable material, of external diameter equal to the internal diameter of the uncompressed ring 24, of internal diameter slightly greater than the diameter of the rod 12 of the piston, and, here, of axial length equal to that of the uncompressed ring 24.
  • the ring 27 is here made of steel, the resistance of which is between 500 and 650 N / m2 and the relative elongation between 15% and 25%.
  • the recess 25 has, in this embodiment, a slightly frustoconical side wall converging towards the front, to better receive the ring 27 and ensure better absorption, further progressive, of the excess energy, the ring coming to marry the wall of the recess.
  • a central bore 28 for receiving the buffer is formed in the buffer guide 7, from its front end face 29, of diameter greater than that of the central bore 26 for passage of the piston rod and into which the central bore opens. rear 26.
  • the sum of the axial lengths of the rigid ring 22, of the compressed intermediate elastic ring 24, and of the buffer guide 7, is slightly greater than the sum of the lengths axial of the frustoconical part 14 of the head and of the rod 12 of the piston 6. Or, the lengths of all these parts are such that the piston 6 cannot protrude outside the buffer guide 7.
  • the arming of the device and the firing are carried out in one case as in the other quite normally.
  • the piston 6 is propelled forward by driving the buffer 4 in the part 1; the frustoconical part 14 of the head abuts against the corresponding bore 23 of the rigid ring 22 ( Figure 2).
  • the rigid ring 22 moves forward, compressing the elastic ring 24 between the front face 30 of the rigid ring 22 and the rear face 31 of the buffer guide 7, the space annular 32, formed around the ring 24, allowing the elastic ring 24 to swell, and by moving the second deformable intermediate ring 27 in the recess 25 in the rear part of the buffer guide 7 (FIG. 3).
  • the energy residue is transmitted by the ring 27 to the buffer guide 7 bearing on the part 1.
  • the axial depth of the recess 25 and the volume of the space 32 are such that at the end of the deformation phase of the elastic ring 24, when the rigid ring 27 abuts against the bottom of the recess 25, the volume of the space 32 has been reduced but is not zero, to avoid constraining the spacer 8.
  • the second rigid intermediate ring 27 under the action of the energy transmitted by the piston, gradually deforms by compression between the front face 30 of the rigid ring 22 and the bottom of the recess 25 of the buffer guide, so that when the device is no longer new, the energy residue is transmitted to the buffer guide only after an axial displacement of the rigid ring 22 slightly greater than the depth of the recess 25.
  • the ring 27 no longer deforms.
  • the axial dimension of the rigid intermediate ring 27 could, in the new state, be smaller than that of the elastic intermediate ring 24, in its uncompressed state, which would avoid having to spare the recess 25 for receiving the ring 27 at the rear of the buffer guide 7.
  • the buffer guide 7 is then either propelled forward if, at the location considered, the support is not under the part, that is to say if it can deform under stress, i.e. the whole device, with the exception initially of the buffer guide and the spacer, moves back under the action of the exhaust gases, the rim 10 of the barrel 51 leaving the rear face of the rigid ring 22 to come into abutment against the rim 9 of the spacer 8 (FIG. 3).
  • the annular space 33 existing between the two flanges 9 and 10, just before firing, aims to allow relative movement of the barrel 51 and the piston 6 and thus avoid a brutal shock at the time of the damping of the piston which can cause inertia parts ruptures.
  • the front end of the rod 12 of the piston 6 remains, here, in relation to the front face 29 of the buffer guide 7. Even if the apparatus is used to pull, so to speak, in a vacuum, that is to say on a thin piece to be fixed in a place where it is not applied on its support, the piston remains inside the device. It is a guarantee of security and quality of the binding.
  • a shock-absorbing device comprising a single rigid monobloc ring 22 and a single elastic monobloc ring 24. It would not be departing from the scope of the present invention to provide, instead of one, several rigid rings and, also instead of 'one, several elastic rings. Similarly, the elastic ring 24 could no longer be outside but inside the rigid deformable ring 27, the recess for receiving the rigid ring, when it is provided, then becoming annular.
  • the ring 22 being able to swell a little, it is preferable that its outside diameter be slightly less than the inside diameter of the spacer 8.
  • the ring 22 must remain guided, we will then spare, on the front part of the ring, a centering and guiding shoulder with an outside diameter substantially equal to the inside diameter of the spacer 8.
  • the opening angle of the frustoconical part 14 of the piston head, and of the corresponding bore 23 of the ring 22, is advantageously between 13 ° and 20 °, and preferably substantially equal to 15 °.
  • the axial dimension of the rigid intermediate ring 27 ⁇ could, in new condition, be greater than that of the elastic intermediate ring 24 ⁇ , in its uncompressed state, provided that the rear recess 25 ⁇ of the guide- pad 7 ⁇ receiving the ring 27 ⁇ is dimensioned accordingly and allows the axial displacement of the ring 27 ⁇ over a length equal to the decrease in the axial dimension of the elastic ring 24 ⁇ after compression ( Figure 4).
  • the axial dimension of the recess 25 ⁇ still remains equal to the difference between the axial dimension of the ring 27 ⁇ and that of the ring 24 ⁇ in its compressed state.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • Portable Nailing Machines And Staplers (AREA)
  • Medicines Containing Material From Animals Or Micro-Organisms (AREA)
  • Saccharide Compounds (AREA)
  • Ventilation (AREA)
  • Cereal-Derived Products (AREA)
  • Inorganic Insulating Materials (AREA)
  • Special Wing (AREA)
  • Specific Sealing Or Ventilating Devices For Doors And Windows (AREA)
  • Vehicle Body Suspensions (AREA)
  • Input Circuits Of Receivers And Coupling Of Receivers And Audio Equipment (AREA)
  • Control Of The Air-Fuel Ratio Of Carburetors (AREA)
EP87402935A 1986-12-23 1987-12-21 Setzgerät mit Treibkolben Expired - Lifetime EP0274957B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR868618018A FR2608493B1 (fr) 1986-12-23 1986-12-23 Appareil de scellement a tir indirect
FR8618018 1986-12-23

Publications (2)

Publication Number Publication Date
EP0274957A1 true EP0274957A1 (de) 1988-07-20
EP0274957B1 EP0274957B1 (de) 1992-05-13

Family

ID=9342190

Family Applications (2)

Application Number Title Priority Date Filing Date
EP87401447A Withdrawn EP0274919A1 (de) 1986-12-23 1987-06-24 Setzgerät mit Treibkolben
EP87402935A Expired - Lifetime EP0274957B1 (de) 1986-12-23 1987-12-21 Setzgerät mit Treibkolben

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP87401447A Withdrawn EP0274919A1 (de) 1986-12-23 1987-06-24 Setzgerät mit Treibkolben

Country Status (14)

Country Link
US (1) US4824003A (de)
EP (2) EP0274919A1 (de)
JP (1) JP2720157B2 (de)
KR (1) KR950005411B1 (de)
AT (1) ATE75985T1 (de)
AU (2) AU598080B2 (de)
CA (1) CA1287699C (de)
DE (1) DE3779092D1 (de)
ES (1) ES2032849T3 (de)
FI (1) FI875680A (de)
FR (1) FR2608493B1 (de)
IE (1) IE59869B1 (de)
NO (1) NO165329C (de)
NZ (1) NZ223012A (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0621110A1 (de) * 1993-04-17 1994-10-26 HILTI Aktiengesellschaft Pulverkraftbetriebenes Setzgerät
EP0732178A1 (de) * 1995-03-17 1996-09-18 Adolf Würth GmbH & Co. KG Bolzensetzgerät
WO1996039282A1 (en) * 1995-06-05 1996-12-12 Sencorp Assembly for deaccelerating a driver in a tool
EP0805002A2 (de) * 1996-05-03 1997-11-05 Beto-Tornado GmbH Pulverkraftbetriebenes Bolzensetzgerät
EP0805003A2 (de) * 1996-05-03 1997-11-05 Beto-Tornado GmbH Pulverkraftbetriebenes Bolzensetzgerät
EP0826464A1 (de) * 1996-09-02 1998-03-04 HILTI Aktiengesellschaft Kolbenrückstellelement für pulverkraftbetriebenes Setzgerät
EP2769808A1 (de) * 2013-02-22 2014-08-27 King Fai Kenneth Kok Entspannungsvorrichtung für Nagelpistolen

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DE3924620A1 (de) * 1989-07-26 1991-01-31 Hilti Ag Pulverkraftbetriebenes bolzensetzgeraet
US5199625A (en) * 1991-09-26 1993-04-06 Illinois Tool Works Inc. Fastener-driving tool assembly with improved fastener-loading features
US5199506A (en) * 1991-09-26 1993-04-06 Illinois Tool Works Inc. Fastener-driving tool assembly with improved fastener-loading features
US5193729A (en) * 1991-09-26 1993-03-16 Illinois Tool Works Inc. Fastener-driving tool assembly with improved fastener-loading features
DE4433410A1 (de) * 1994-09-20 1996-03-21 Hilti Ag Bolzensetzgerät
FR2746690B1 (fr) * 1996-03-26 1998-05-29 Spit Soc Prospect Inv Techn Appareil d'entrainement de tampon par masselotte a retour automatique en position du tir
DE19638341A1 (de) 1996-09-19 1998-03-26 Wuerth Adolf Gmbh & Co Kg Bolzenschubgerät und Feder dafür
US7111767B2 (en) * 1997-04-24 2006-09-26 Simpson Strong-Tie Company, Inc. Power actuated fastener system
US5897045A (en) * 1997-09-12 1999-04-27 Illinois Tool Works Inc. Fastener dispensing apparatus for stand-up fastener driving tool and method therefor
US5918789A (en) * 1997-09-12 1999-07-06 Illinois Tool Works Inc. Fastner collation tube for stand-up fastener driving tool
DE19800847A1 (de) * 1997-12-04 1999-06-17 Gerd Dr Ing Kellner Gerät zum Setzen eines Befestigungselementes in einen Setzuntergrund und Verwendung des Gerätes
US6171042B1 (en) 1997-12-19 2001-01-09 Illinois Tool Works Inc. Hardened steel pin, pin and washer fastener, washer for fastener, and pin-making method
US6006704A (en) * 1997-12-31 1999-12-28 Porter-Cable Corporation Internal combustion fastener driving tool fuel metering system
US6260519B1 (en) * 1997-12-31 2001-07-17 Porter-Cable Corporation Internal combustion fastener driving tool accelerator plate
US6016946A (en) * 1997-12-31 2000-01-25 Porter-Cable Corporation Internal combustion fastener driving tool shuttle valve
US6158643A (en) * 1997-12-31 2000-12-12 Porter-Cable Corporation Internal combustion fastener driving tool piston and piston ring
US6045024A (en) * 1997-12-31 2000-04-04 Porter-Cable Corporation Internal combustion fastener driving tool intake reed valve
US6041603A (en) * 1997-12-31 2000-03-28 Porter-Cable Corporation Internal combustion fastener driving tool accelerator plate
USD410182S (en) 1997-12-31 1999-05-25 Porter-Cable Corporation Internal combustion fastener driving tool
US20030057248A1 (en) * 1999-09-10 2003-03-27 Bruins Roger C. Automatic washer feeder for automatic nailer
US6092710A (en) * 1998-06-09 2000-07-25 Berner Gmbh Explosive powder charge operated bolt-setting tool
US6257352B1 (en) * 1998-11-06 2001-07-10 Craig Nelson Rock breaking device
JP3622193B2 (ja) * 1999-03-04 2005-02-23 マックス株式会社 釘打機、タッカ等のバンパ
DE19947464A1 (de) * 1999-10-02 2001-04-05 Hilti Ag Bolzensetzgerät zum Eintreiben von Bolzen oder dergleichen in Bauteile
US6779700B2 (en) * 2000-02-18 2004-08-24 National Nail Corp. Cap assembly and cap feeder for automatic fastener driver
CN1329164C (zh) * 2001-09-17 2007-08-01 密尔沃基电动工具公司 旋转锤
US6679411B2 (en) * 2001-12-21 2004-01-20 Illinois Tool Works Inc. Piston retention system for a fastener driving tool
US20030133768A1 (en) * 2002-01-11 2003-07-17 Alfonso Losada Fastener assembly having grooves for use with a power actuated gun
US20040188489A1 (en) * 2002-10-18 2004-09-30 Alfonso Losada Power actuated gun with automatic firing
US7249701B2 (en) * 2002-11-05 2007-07-31 Simpson Strong-Tie Co., Inc. Power actuated gun with fastener feeding track and automatic firing
DE10341385B4 (de) * 2003-09-05 2016-06-23 Hilti Aktiengesellschaft Setzgerät
DE10341384B4 (de) * 2003-09-05 2016-06-23 Hilti Aktiengesellschaft Setzgerät
US7726536B2 (en) * 2004-04-02 2010-06-01 Black & Decker Inc. Upper bumper configuration for a power tool
DE102005000106B4 (de) * 2005-08-25 2014-02-27 Hilti Aktiengesellschaft Setzgerät
DE102005000114A1 (de) * 2005-09-13 2007-03-15 Hilti Ag Setzgerät
DE102005000113B4 (de) * 2005-09-13 2014-03-27 Hilti Aktiengesellschaft Setzgerät
DE102010030127A1 (de) * 2010-06-15 2011-12-15 Hilti Aktiengesellschaft Eintreibvorrichtung
WO2016176725A1 (en) * 2015-05-01 2016-11-10 Kinetic Pressure Control Limited Blowout preventer
EP3314059A4 (de) * 2015-06-29 2019-03-27 Terminator IP Limited Stossabsorbierende werkzeugverbindung
DE102021132912A1 (de) 2021-12-14 2023-06-15 Carl Freudenberg Kg Dämpfungselement und Bolzensetzgerät, das ein solches Dämpfungselement umfasst

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FR1344304A (fr) * 1961-09-08 1963-11-29 Outils d'ancrage perfectionnés, actionnés par explosif
FR1355370A (fr) * 1962-05-07 1964-03-13 Impex Essen Vertrieb Appareil destiné à l'enfoncement de chevilles dans des éléments de construction fixes ou autres
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Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB934082A (en) * 1960-08-11 1963-08-14 Olin Mathieson Improvements in explosive actuated fastener driving tools
FR1344304A (fr) * 1961-09-08 1963-11-29 Outils d'ancrage perfectionnés, actionnés par explosif
FR1355370A (fr) * 1962-05-07 1964-03-13 Impex Essen Vertrieb Appareil destiné à l'enfoncement de chevilles dans des éléments de construction fixes ou autres
DE1478838A1 (de) * 1965-11-09 1969-01-30 Bauer Carl Fa Bolzensetzgeraet zum Eintreiben von Bolzen od.dgl. in Bauteile
DE2007984A1 (de) * 1970-02-20 1971-09-02 Olin Corp., New Haven, Conn. (V.St.A.) Treibmittelbetätigtes Bolzensetzgerät
US3746235A (en) * 1972-01-12 1973-07-17 Olin Corp Power control for powder-actuated tool
AU447009B2 (en) * 1972-01-12 1974-03-21 Olin Corporation Power actuated tool
US4493376A (en) * 1982-07-02 1985-01-15 Uniset Corporation Fastener driving tool

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0621110A1 (de) * 1993-04-17 1994-10-26 HILTI Aktiengesellschaft Pulverkraftbetriebenes Setzgerät
EP0732178A1 (de) * 1995-03-17 1996-09-18 Adolf Würth GmbH & Co. KG Bolzensetzgerät
EP0995552B1 (de) * 1995-03-17 2007-05-02 Adolf Würth GmbH & Co. KG Bolzensetzgerät
EP0995552A2 (de) * 1995-03-17 2000-04-26 Adolf Würth GmbH & Co. KG Bolzensetzgerät
WO1996039282A1 (en) * 1995-06-05 1996-12-12 Sencorp Assembly for deaccelerating a driver in a tool
EP0805003A3 (de) * 1996-05-03 1998-02-04 Beto-Tornado GmbH Pulverkraftbetriebenes Bolzensetzgerät
EP0805002A3 (de) * 1996-05-03 1998-01-14 Beto-Tornado GmbH Pulverkraftbetriebenes Bolzensetzgerät
EP0805003A2 (de) * 1996-05-03 1997-11-05 Beto-Tornado GmbH Pulverkraftbetriebenes Bolzensetzgerät
US6085958A (en) * 1996-05-03 2000-07-11 Berner Gmbh Explosive powder charge operated bolt-setting tool
US6123242A (en) * 1996-05-03 2000-09-26 Berner Gmbh Explosive powder charge operated bolt-setting tool
EP0805002A2 (de) * 1996-05-03 1997-11-05 Beto-Tornado GmbH Pulverkraftbetriebenes Bolzensetzgerät
EP0826464A1 (de) * 1996-09-02 1998-03-04 HILTI Aktiengesellschaft Kolbenrückstellelement für pulverkraftbetriebenes Setzgerät
EP2769808A1 (de) * 2013-02-22 2014-08-27 King Fai Kenneth Kok Entspannungsvorrichtung für Nagelpistolen

Also Published As

Publication number Publication date
NO165329C (no) 1991-01-30
AU8286887A (en) 1988-06-23
JPS63229275A (ja) 1988-09-26
NO165329B (no) 1990-10-22
US4824003A (en) 1989-04-25
NO875382D0 (no) 1987-12-22
EP0274919A1 (de) 1988-07-20
JP2720157B2 (ja) 1998-02-25
ATE75985T1 (de) 1992-05-15
IE59869B1 (en) 1994-04-20
DE3779092D1 (de) 1992-06-17
NZ223012A (en) 1989-11-28
AU598080B2 (en) 1990-06-14
ES2032849T3 (es) 1993-03-01
CA1287699C (en) 1991-08-20
FI875680A0 (fi) 1987-12-22
EP0274957B1 (de) 1992-05-13
KR950005411B1 (ko) 1995-05-24
FR2608493A1 (fr) 1988-06-24
FI875680A (fi) 1988-06-24
AU630071B2 (en) 1992-10-22
FR2608493B1 (fr) 1994-09-02
KR880007179A (ko) 1988-08-26
NO875382L (no) 1988-06-24
IE873492L (en) 1988-06-23

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