US3566978A - Apparatus for driving anchoring elements for a predetermined depth of penetration - Google Patents

Apparatus for driving anchoring elements for a predetermined depth of penetration Download PDF

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Publication number
US3566978A
US3566978A US792033*A US3566978DA US3566978A US 3566978 A US3566978 A US 3566978A US 3566978D A US3566978D A US 3566978DA US 3566978 A US3566978 A US 3566978A
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US
United States
Prior art keywords
hammer piston
stop member
housing
housing member
penetration
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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
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US792033*A
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English (en)
Inventor
Karl-Ernst Udert
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Hilti AG
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Hilti AG
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Filing date
Publication date
Application filed by Hilti AG filed Critical Hilti AG
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Publication of US3566978A publication Critical patent/US3566978A/en
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    • 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 strength of the target material is not uniform, for example, in steel characterized as St37 the strength can range between 37 -45 kp/qmm, and further, the thicknesses of the cartridges employedalso effects the depth of penetration achieved. Accordingly, based on the. strength of the target material at thepoint of insertion of the anchoring element and also the thicknesstof.thecartridge used in driving the anchoringelement, the depth of penetration into the target material will vary. In certain methods of fastening anchoring elements this inability. to provide a, reproducible: depth of penetration is disadvantageous. If: it is attemptedto. obtain a uniform depth of penetration with known guns of the; type mentioned above, for example, by varying the initial. combustion space, then, initially, it would be necessary to; determine the strength of the target material at the point of insertion of the anchoring element. Such. an arrangement for:
  • the primary object of the present invention is to provide an arrangement for achievinga reproducible depth of penetration of anchoring elements into a target material.
  • Another object of the invention is to usean excess amount of kinetic energy in driving the anchoringelement intothe tar.- get material and, after the insertion of the anchoring element-,. transforming at least a major portion of the excess kinetic energy into thermal energy.
  • Still another object of the invention is to provide a spring arrangement for. absorbing a portion of. the excess energy employed in driving the anchoring elements.
  • Yet another object of the invention is to supply the driving. piston and a stop member with frustoconically shaped surfaces for frictional interengagement when the hammer piston has driven the anchoring element into the target material for a. predetermined depth.
  • kinetic energy is transmitted to a hammer piston ina quantity in excess of that required to provide a predetermined reproducible-depth of penetration of the anchoring elements.
  • the excess kinetic energy is transformed into thermal energy when the hammer piston passes into frictional. contact with a suitably shaped stop member.
  • the stop member is elastically deformable and the thermal energy is developed due to the frictional contact between the hammer piston and the stop member as the stop member'travels througha short path because of its elastic deformation. Any residual kinetic. energy transferred from the hammer piston to the stop. member and nottransferred into thermal energy is transmitted to means operatively positionedbetween the stop memberandf the housing.
  • the excess kinetic energy transmitted to the hammer piston is greater than that necessary to achieve the depth of penetration, the required depth of penetration of the anchoring element is obtainable in every instance. Accordingly, once the anchoring element has been driven to the predetermined depth by the hammer piston the excess kinetic energy can be removed from the hammer piston. In the present invention it has been recognized that it is advantageous to transform a major portion of the excess kinetic energy, for example, about two-thirds, into thermal energy.
  • the change of the kinetic energy supplied to the hammer piston into thermal energy is accomplished by affording frictional contact between the hammer piston and'a stop member against whichthe hammer piston impacts when it has attained the desired depth of penetration for the anchoring elements.
  • the hammer piston is arranged to extend through the stop member in achieving theiinsertion of the anchoringelement.
  • the residual portion of the excess kinetic energy, which. is. nottransformed into thermalgenergy, is transmitted to a body in operative connection with the housing partwhose mass is of such anextent that the inertia of the body is sufficient to absorb the residual kinetic energy.
  • both the hammer pistonv and the stop member are each provided with a frustoconically shaped surface converging in the firing direction of thedevice with the surfaces arranged-to be in frictional contact after the desired depth of penetration of the anchoring element has been.
  • the elastically defonnable stop member is supported within the device by the member which is arranged to absorb the excess kineticenergy not transformed into thermal energy.
  • the stop member is provided with a second frustoconically arranged surfacediverging in the firing direction and mounted on a frustoconically shaped inner ring to provide both elastic. deformation and'axialdisplacement.
  • the inner ring bears directly against the member within the housing which absorbs the excess kinetic energy from the stop member.
  • Another feature of the apparatus in accordance with the present invention, concerns the possible damage to impactsensitive materials, such as wood, plastics, and the like, and
  • a pair of spring members are disposed within the housing for absorbing or resiliently mounting the various parts of the apparatus within the housing.
  • These annular springs and, in addition, the inner and outer rings afford a transformation of the excess energy into thermal energy.
  • a guide member is provided at the firing end which is axially displaceable within the housing under the impact provided by the hammer piston to avoid damage to the target material.
  • the guide member is connected to the housing preferably by means of a catch.
  • the force of the catch is so great that the contact pressure is overcome, without the guide part being displaced relative to the housing part.
  • the hammer piston can be adjusted preferably by varying it to a minor extent by shifting the housing part containing the piston and stop member.
  • FIG. 1 is a longitudinal sectional view of the front or firing end of a device for inserting anchoring elements illustrating one embodiment of the invention
  • FIG. 2 is a longitudinal sectional view similar to that shown in FIG. 1 illustrating a second embodiment of the present invention.
  • FIG. 3 is a longitudinal sectional view of an alternate arrangement for securing the forward end of the device, shown in FIGS. 1 and 2, in position.
  • a device 3 for inserting anchoring elements into a target material is formed of a housing member 1 secured to the device 3 by means of threads 2. Located in the forward or firing end of the housing member 1 is a guide member 4 for aligning the anchoring elements prior to the insertion operation.
  • a member 5 is secured to the housing member by shear pins 6. The member 5 extends transversely across the housing member 1. In its rearward face a recess 5a is formed in the member 5 and an opening 5b extends forwardly from the recess through the member.
  • a stop member 7 Located within the recess 5a is a stop member 7 with a certain amount of radial play provided between the outer periphery of the stop member and the juxtaposed surface of the recess.
  • a hole or opening 7' is formed through the stop member 7 coaxial with the opening 511 through the member 5.
  • the rearward portion of the opening 7 has a frustoconically shaped surface 7 a which is in converging relationship in the firing direction of the device.
  • a hammer piston 8 Mounted for axial displacement through the device 3 and the housing member I is a hammer piston 8 which, as shown in FIG. I, has its forward end supported within the guide member 4.
  • the hammer piston 8 Near its rearward end the hammer piston 8 has a frustoconically shaped surface portion 8a which is arranged to engage the correspondingly tapered surface 7a of the stop member 7.
  • the surface 7a within the stop member and the surface 8a on the hammer piston are arranged in contacting engagement when the hammer piston is driven forwardly through the device 3 by an explosive force for driving an anchoring element, not shown, from the guide member 4 of the device.
  • shear pins 6 are dimensioned to shear when considerable excess energy is developed in the member 5 and before any of the other parts in the device are overstressed and damaged.
  • FIG. 2 a second embodiment of the invention is set forth which operates in generally the same manner as the embodiment in FIG. 1, however, the arrangement is somewhat more elaborate and provides for a greater absorption of excess energy by spring means within the housing member.
  • This second embodiment is formed of a housing member 101 engaged by means of threads 102 on the front end of a device 103. At the forward or firing end of the housing member a guide member 104 is resiliently positioned.
  • a member 105 is positioned within the rearward interior end of the housing member 101 .
  • the member 105 has an axially arranged recess 105a extending forwardly from its rearward end and being axially located relative to the housing member 101.
  • a stop member 107 Positioned within the recess 105a is a stop member 107 having an axial opening 107' extending therethrough and aligned with a similar opening 105k in the forward end of the member 105.
  • the opening through the stop member 107 has a first frustoconically shaped surface 107a and a second serially arranged frustoconically shaped surface l07b.
  • the surface 107a extends from the rearward end of the stop member for a portion of its length and the remainder of the opening through the stop member is provided by the second surface l07b. While the surface 107a converges in the firing direction the second surface 107k diverges in the firing direction and provides an open space within which a frustoconically shaped ring member is positioned having its opening in axial alignment with the the frictional through the device 107 and the housing member 101.
  • the hammer piston passes axially through thespring 107 in the stop member, the opening in the ring member 11512, the opening 105 in-the member 105 and the guidemember 104. Near its rear end the hammer piston 108 .has a frustoconically shaped surface 108a, converging in the firing direction, which impacts against the surface 107a of the stop member 107.
  • the member 105 At its forward end the member 105 has a smaller outside diameter than its rear 'portion providing an annular space between its outer surface and the opposite inner surface of the housing member 101.
  • a plurality of inner rings 110 and outerrings 111 disposed in an alternating arrangement.
  • the outer face s of theinner rings and the inner faces of the outer rings taper in both directions from a midpoint.
  • the tapered faces of the alternating inner and outer rings each contacts a similarly tapered surfaceon the adjacentrings, for example each full inner ring contacts two outer rings, one
  • a half inner ring 110a bears against the'member 105 while at the opposite end of the rings a half outer ring 111a .bears against asleevelike member 113 whichhas a diameter. slightly less than that of the inner rings so that it is positioned inwardly of the rings.
  • the sleevelike member 113 has a radially outwardly directed flange 113a which extends into contact with the inner surface of the housing member 101.
  • the sleevelike member 113 At its rearward end the sleevelike member 113-has a radially inwardly :directed flange 113b which extends inwardly toward but is spaced from the outersurface of the guide member 104 at its rearward end.
  • a first helical spring 114 bears against the inner forward face of the housing member 101 and extends rearwardly within the sleeve 113 and bears against the flange 11312.
  • Spaced inwardly from the first spring 114 is a second helical spring 116 which bears against a shoulderformed on the guide member 104 and extends rearwardly and bears against the member 105 within a recess 105c'formed in its for ward face.
  • the housing member 101 is in threaded engagement with the remainder of the device 103. to afford a fine adjustment for the hammer piston stroke.
  • a screw 120 can be engaged within a slot 103a in the threaded end of the device 103 to assure that the housing member 101 is secured against any accidental turning and displacement.
  • the hammer piston 1.03 rides forwardly guided within the bore through the device 103, the ring 115, and the guide member 104 for inserting an anchoring member into a target material. Since the explosive force which drivesthe hammer piston forwardly through the device supplies an amount of kinetic energy in excess of that required for driving the anchoring element for its predetermined depth of penetration, when the predetermined depth of penetration has been achieved, the frustoconically shaped surface 108a on the hammer piston impacts against the similarly shapedsurface 107a of the stop member and elastically deforms the stop member.
  • the force or energy exerted on the member 105 tends to press forwardly against the spring 116 which bears at its forward end against the guide member 104.
  • the member 105 also exerts a force in the forward direction against the combined inner and outer rings 110, 111 which at their forward end bear against the flange 113a of the sleeve member 113.
  • the inner and outer rings ride forwardly with the sleeve 113 for distance a compressingthe helical spring 114 until the flange 113a contacts the forward end of the housing member 101 and then the the housing member 201 and the guide 204 which can be employed in guns or devices with a pressure safety device.
  • a number of bores 221 extend through the forward end face of the housing member201 and open at their inner ends into a groove or recess 204a, formed in the exterior surface of the guide member 204.
  • a ball222 is inserted into each bore 221 and a spring member 223 held in place by a retaining pin 224 resiliently urges the ball into locking engagement with the recess 204a and'etains the guide part within the forward end of the housing member.
  • Apparatus for driving anchoring elements such as bolts, studs, and nails into a hard target material such'as iron, concrete and the like to obtain a predetermined reproducible depth of penetration of the anchoring elements comprises a housing member, a hammer piston axially displaceably mounted within said housing memherfor driving anchoring elements into the target material in response to an explosive force acting on said hammer piston, means mounted within said housing arrl arranged for receiving energy from said hammer piston, a stop member mounted within said housing and in contact with said means within said housing member, said stop member is elastically deformable and is arranged to be in frictional contact with said hammer piston when said hammer piston has a effected the predetermined depth of penetration of the anchoring elements and said stop member also being in bearing contact with said means when it is in frictional contact with said hammer piston, resilient means being positioned within said housing member for mounting said means inaxially displaceable relationship within said housing member, said resilient means comprisesa plurality of inner rings and a plurality
  • said resilient means comprises a sleeve located within said housing member and spaced inwardly from the inner surface of said inner rings, a radially outwardly extending flange secured to the forward end of said sleeve in the firing direction of the apparatus and extending outwardly into sliding contact with the inner surface of said housing member, at the rearward end of the alternating said inner and outer rings the rearward one thereof contacting said member and at the forward end of said inner and outer rings the forward one thereof contacting said flange on said sleeve.
  • Apparatus as set forth in claim 3, wherein an axially displaceable guide member being located in the forward end of said housing member in the firing direction of said apparatus.
  • said resilient means comprises a first helical spring extending between said sleeve and the inner surface of said housing member at its forward end, and a second helical spring extending between said member at the forward end thereof and said guide member.
  • Apparatus for driving anchoring elements such as bolts, studs, and nails into a hard target material such as iron, concrete and the like to obtain a predetermined reproducible depth of penetration of the anchoring elements comprises a housing member, a hammer piston axially displaceably mounted within said housing member for driving anchoring elements into the target material in response to an explosive force acting on said hammer piston, means mounted within said housing and being arranged for receiving energy from said hammer piston, a stop member mounted within said housing and in contact with said means within said housing member, said stop member is elastically deformable and is arranged to be in frictional contact with said hammer for when said hammer piston has effected the predetermined depth of penetration of the anchoring elements and said stop member also being in bearing contact with said means when it is in frictional contact with said hammer piston, said stop member comprises a first annular part anda second annular part, said second annular part being disposed within said first annular part and located at the end thereof extending in the firing direction of the apparatus,
  • said means cornlprisin a member mounted in said housing member to be axia disp aceable therein, said member having an axially arranged recess in the end thereof directed away from the firing direction of the apparatus, said stop member being spaced within and radially inwardly from the recess in said member for permitting widening of said stop member within said recess.
US792033*A 1968-01-29 1969-01-17 Apparatus for driving anchoring elements for a predetermined depth of penetration Expired - Lifetime US3566978A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1603852A DE1603852C3 (de) 1968-01-29 1968-01-29 Abfangvorrichtung für den Eintreibkolben eines pulverkraftbetriebenen Bolzensetzgerätes
DEH0065155 1968-01-29

Publications (1)

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US3566978A true US3566978A (en) 1971-03-02

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US792033*A Expired - Lifetime US3566978A (en) 1968-01-29 1969-01-17 Apparatus for driving anchoring elements for a predetermined depth of penetration

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US (1) US3566978A (de)
DE (1) DE1603852C3 (de)
FR (1) FR1595405A (de)
GB (1) GB1242458A (de)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3871565A (en) * 1972-02-23 1975-03-18 Pierre Termet Cartridge-fired apparatus for driving fasteners and the like
US3881554A (en) * 1973-05-25 1975-05-06 William C Cooley Mechanically actuated hammer and bit assembly therefor
US4082151A (en) * 1977-01-14 1978-04-04 Hughes Tool Company Cam mounting for an impact tool
US4122987A (en) * 1976-07-19 1978-10-31 Hilti Aktiengesellschaft Damping device for a fastening element setting gun
US4222462A (en) * 1978-10-11 1980-09-16 Ottestad Jack Benton Brake to decelerate axially moving actuating rod
US4558747A (en) * 1982-08-11 1985-12-17 Cunningham James D Impact devices
US4824003A (en) * 1986-12-23 1989-04-25 Societe De Prospection Et D'inventions Techniques S.P.I.T. Indirect firing fastener driving tool
US4838363A (en) * 1985-11-04 1989-06-13 Quarry Engineering Developments Pty. Ltd. Rock-breaking apparatus
EP0732178A1 (de) * 1995-03-17 1996-09-18 Adolf Würth GmbH & Co. KG Bolzensetzgerät
US5755294A (en) * 1995-04-14 1998-05-26 Hyup Sung Heavy Industries Co., Ltd. Abrasion-resistant hydraulic hammer with low noise level
US6098723A (en) * 1997-09-08 2000-08-08 Chicago Pneumatic Tool Company Reciprocating tool having a piston retainer
US6257352B1 (en) 1998-11-06 2001-07-10 Craig Nelson Rock breaking device
FR2859404A1 (fr) * 2003-09-05 2005-03-11 Hilti Ag Outil de scellement
US6889884B2 (en) * 2001-01-30 2005-05-10 Hilti Aktiengesellschaft Setting tool
US20080217039A1 (en) * 2007-03-08 2008-09-11 Hilti Aktiengesellschaft Hand-held power tool with a pneumatic percussion mechanism
US20100126746A1 (en) * 2006-12-07 2010-05-27 Rocktec Limited Breaking machine shock absorbing system
US9278443B2 (en) 2006-12-07 2016-03-08 Terminator Ip Limited Breaking machine shock absorbing apparatus
US20180236647A1 (en) * 2017-02-22 2018-08-23 Illinois Tool Works Inc. Fastener pusher with an improved workpiece-contact element

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3924620A1 (de) * 1989-07-26 1991-01-31 Hilti Ag Pulverkraftbetriebenes bolzensetzgeraet

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2308143A (en) * 1941-12-03 1943-01-12 Chicago Pneumatic Tool Co Snubber for tamper bars
US2836247A (en) * 1954-05-17 1958-05-27 Exxon Research Engineering Co Extension of effective length of tubing
US2845908A (en) * 1957-04-12 1958-08-05 Olin Mathieson Buffer mechanism
GB858618A (en) * 1958-05-20 1961-01-11 Olin Mathieson Buffer mechanism
US3016539A (en) * 1957-06-25 1962-01-16 Olin Mathieson Powder actuated tool
US3115637A (en) * 1961-08-11 1963-12-31 Olin Mathieson Explosive actuated fastener driving tools
US3297224A (en) * 1965-04-30 1967-01-10 Olin Mathieson Power actuated tool
US3465942A (en) * 1965-11-09 1969-09-09 Bauer Carl Fastener driving tool
US3469504A (en) * 1963-08-26 1969-09-30 Omark Industries Inc Impact dissipating device

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2308143A (en) * 1941-12-03 1943-01-12 Chicago Pneumatic Tool Co Snubber for tamper bars
US2836247A (en) * 1954-05-17 1958-05-27 Exxon Research Engineering Co Extension of effective length of tubing
US2845908A (en) * 1957-04-12 1958-08-05 Olin Mathieson Buffer mechanism
US3016539A (en) * 1957-06-25 1962-01-16 Olin Mathieson Powder actuated tool
GB858618A (en) * 1958-05-20 1961-01-11 Olin Mathieson Buffer mechanism
US3115637A (en) * 1961-08-11 1963-12-31 Olin Mathieson Explosive actuated fastener driving tools
US3469504A (en) * 1963-08-26 1969-09-30 Omark Industries Inc Impact dissipating device
US3297224A (en) * 1965-04-30 1967-01-10 Olin Mathieson Power actuated tool
US3465942A (en) * 1965-11-09 1969-09-09 Bauer Carl Fastener driving tool

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3871565A (en) * 1972-02-23 1975-03-18 Pierre Termet Cartridge-fired apparatus for driving fasteners and the like
US3881554A (en) * 1973-05-25 1975-05-06 William C Cooley Mechanically actuated hammer and bit assembly therefor
US4122987A (en) * 1976-07-19 1978-10-31 Hilti Aktiengesellschaft Damping device for a fastening element setting gun
US4082151A (en) * 1977-01-14 1978-04-04 Hughes Tool Company Cam mounting for an impact tool
US4222462A (en) * 1978-10-11 1980-09-16 Ottestad Jack Benton Brake to decelerate axially moving actuating rod
US4558747A (en) * 1982-08-11 1985-12-17 Cunningham James D Impact devices
US4838363A (en) * 1985-11-04 1989-06-13 Quarry Engineering Developments Pty. Ltd. Rock-breaking apparatus
US4824003A (en) * 1986-12-23 1989-04-25 Societe De Prospection Et D'inventions Techniques S.P.I.T. Indirect firing fastener driving tool
EP0732178A1 (de) * 1995-03-17 1996-09-18 Adolf Würth GmbH & Co. KG Bolzensetzgerät
US5755294A (en) * 1995-04-14 1998-05-26 Hyup Sung Heavy Industries Co., Ltd. Abrasion-resistant hydraulic hammer with low noise level
US6098723A (en) * 1997-09-08 2000-08-08 Chicago Pneumatic Tool Company Reciprocating tool having a piston retainer
US6257352B1 (en) 1998-11-06 2001-07-10 Craig Nelson Rock breaking device
US6889884B2 (en) * 2001-01-30 2005-05-10 Hilti Aktiengesellschaft Setting tool
FR2859404A1 (fr) * 2003-09-05 2005-03-11 Hilti Ag Outil de scellement
US20100126746A1 (en) * 2006-12-07 2010-05-27 Rocktec Limited Breaking machine shock absorbing system
US8181716B2 (en) * 2006-12-07 2012-05-22 Terminator Ip Sa Breaking machine shock absorbing system
US9278443B2 (en) 2006-12-07 2016-03-08 Terminator Ip Limited Breaking machine shock absorbing apparatus
US20080217039A1 (en) * 2007-03-08 2008-09-11 Hilti Aktiengesellschaft Hand-held power tool with a pneumatic percussion mechanism
US20180236647A1 (en) * 2017-02-22 2018-08-23 Illinois Tool Works Inc. Fastener pusher with an improved workpiece-contact element
US10888985B2 (en) * 2017-02-22 2021-01-12 Illinois Tool Works Inc. Fastener pusher with an improved workpiece-contact element

Also Published As

Publication number Publication date
DE1603852B2 (de) 1975-04-17
FR1595405A (de) 1970-06-08
DE1603852C3 (de) 1975-12-04
GB1242458A (en) 1971-08-11
DE1603852A1 (de) 1971-09-30

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