EP1716979A1 - Marteau perforateur ou marteau-burineur - Google Patents

Marteau perforateur ou marteau-burineur Download PDF

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Publication number
EP1716979A1
EP1716979A1 EP06112584A EP06112584A EP1716979A1 EP 1716979 A1 EP1716979 A1 EP 1716979A1 EP 06112584 A EP06112584 A EP 06112584A EP 06112584 A EP06112584 A EP 06112584A EP 1716979 A1 EP1716979 A1 EP 1716979A1
Authority
EP
European Patent Office
Prior art keywords
contact point
firing pin
percussion
impact
drill
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
EP06112584A
Other languages
German (de)
English (en)
Other versions
EP1716979B1 (fr
Inventor
Michael Schamberger
Erwin Manschitz
Christian Daubner
Josef Bauer
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.)
Hilti AG
Original Assignee
Hilti 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 Hilti AG filed Critical Hilti AG
Publication of EP1716979A1 publication Critical patent/EP1716979A1/fr
Application granted granted Critical
Publication of EP1716979B1 publication Critical patent/EP1716979B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • B25D17/06—Hammer pistons; Anvils ; Guide-sleeves for pistons
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D11/00—Portable percussive tools with electromotor or other motor drive
    • B25D11/06—Means for driving the impulse member
    • B25D11/12—Means for driving the impulse member comprising a crank mechanism
    • B25D11/125—Means for driving the impulse member comprising a crank mechanism with a fluid cushion between the crank drive and the striking body
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
    • B25D2217/0011—Details of anvils, guide-sleeves or pistons
    • B25D2217/0015—Anvils
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
    • B25D2250/245—Spatial arrangement of components of the tool relative to each other

Definitions

  • the invention relates to a drill or chisel hammer with a striking mechanism, referred to in the preamble of claim 1.
  • a firing pin also called an anvil
  • a contact point and a counter contact point are provided.
  • the percussion means is designed as a motor-driven exciter piston, which strikes the transmission of a shock pulse directly on the, the impact means facing the end of the firing pin, wherein the contact point and the mating contact point come into contact.
  • a striking mechanism with a pneumatically driven percussion piston known.
  • a motor-driven exciter or drive piston and a percussion piston also called a free piston, is provided, wherein an air cushion is formed between the drive piston and the percussion piston.
  • the percussion piston Due to the reciprocating movement of the drive piston, the percussion piston is displaced in a phase-shifted manner as well, and this acts on the firing pin and the contact point and the counter-contact point come into contact with each other. If the reciprocating motion of the drive piston is stimulated by an electric motor, these impact mechanisms become electropneumatic impactors designated. Electropneumatic impactors are widely used and are used in various performance categories of rotary and chipping hammers.
  • a disadvantage of the known solution is that when breakthrough of the tool by the machined substrate or when lifting the tool from the ground look up the percussion piston and the firing pin. It should be noted that in the active operating state of the drill or chisel, when the tool is in contact with the ground, the percussion piston and the firing pin cover only a short distance in the guide tube, while in the passive operating state of the drill or chisel, when the tool breaks through the ground or the tool is lifted from the ground, the percussion piston and the firing pin travel a distance in the guide tube, which can correspond to 20 times the distance during the active operating state.
  • the firing pin In order to prevent the so-called looking up of the percussion piston, the firing pin and thus also arranged in the drill or chisel tool or at least limit, in a pneumatic percussion a free travel is provided at least for the percussion piston and the firing pin.
  • Ventilation openings are provided on the guide tube for this purpose. If the tool z. B. lifted from the ground, the sealing means on the percussion piston passes over these ventilation openings, wherein the air cushion between the percussion piston and the excitation piston is reduced, so that no further impact on the tool.
  • High performance rotary or chipping hammers are much more likely to look up than lower performance machines, so a relatively long free travel in hammers or chisel hammers with a high single impact energy to prevent lookup must be provided. This requires a correspondingly long design of the drill or chisel hammer, which, however, in particular for ergonomic reasons, for. B. due to the high weight or handling of the drill or chisel hammer, is undesirable.
  • the kinetic energy of the percussion means, of the firing pin and also of the tool is additionally reduced by friction of the same in their guides.
  • the energy of these components is degraded so far that they no longer move the percussion piston from its parking position in which the air cushion is vented, and the ventilation openings are closed again.
  • the ventilation openings are closed again.
  • a firing pin brake In a very high single impact energy generating drill or chisel hammer therefore additional and structurally complex measures such.
  • a percussion piston brake or catching devices are provided in the percussion to prevent the lookup.
  • a firing pin brake is known in which the firing pin is held in the passive operating state in its ineffective position by means of a locking, resilient clamping ring.
  • the object of the invention is to provide a drill or chisel hammer with a percussion, in which a lookup of the percussion means, the firing pin and thus the tool is structurally simple and inexpensive prevented even at high single impact energy of the drill or chisel.
  • the contact point is exposed and arranged outside the striking axis.
  • the lookup can be prevented.
  • the drill or chisel hammer can be made shorter and accordingly has a comparably low total weight. Even if wear should occur in the guides, on the firing pin or on the percussion means, the function of these parts and thus of the drill or chisel hammer over the service life is ensured by the structurally simple design. Overall, the solution according to the invention is very cost-effective, since no additional components or expensive processing steps are required for their realization.
  • ventilation openings are provided on the guide tube in this percussion mechanism for venting the air cushion in the passive operating state of the chisel hammer.
  • contact point and counter contact point do not mean points in the mathematical sense, but contact regions which correspond to the surfaces which are formed when the impact element meets the striker. Outside, an eccentric or offset to the impact axis arrangement of the contact point is based on its center understood, the distance to the impact axis corresponds to an amount that is greater than the usual manufacturing tolerances. It is also conceivable that a region of the contact point, d. H. a part of the contact surface of the percussion means with the firing pin, is penetrated by the striking axis.
  • the contact point on the firing pin is provided at its, the impact means end facing.
  • the firing pin for example, at its end facing the impact means a convex, the impact means facing survey, the culmination point protrudes from a plane defined by a peripheral edge of the firing pin level and is located outside the percussion axis.
  • the survey is z.
  • the contact point is designed as a protruding body over the plane spanned by the peripheral edge of the firing pin, for example as a cylindrical section.
  • the contact point on the impact means is provided on its side facing the firing pin.
  • the firing pin facing side of the impact means for example, convex, wherein the culmination point of the survey created thereby opposite the peripheral edge of the firing pin facing side of the percussion means plane protrudes and is arranged outside the striking axis.
  • the survey may also have any shape and is z. B. formed as a parabolic curvature first nourishment or as a protruding cuboid portion.
  • the mating contact point may also be exposed and arranged outside the striking axis, wherein the configuration of the mating contact point does not necessarily have to correspond to the configuration of the contact point.
  • the contact point is arranged at a distance to the impact axis which corresponds to 0.003 to 0.05 times the axial length of the firing pin, whereby an increased friction between the percussion and the firing pin with the corresponding guide for the reduction of kinetic energy, at a negligible compared to a percussion, in which the percussion means centrically strikes on the firing pin is increased is generated.
  • Particularly advantageous in terms of the relationship between the achieved degradation of the kinetic energy, the impairment of momentum transfer and the wear of the guides has proven to be a distance that corresponds to 0.005 to 0.03 times the axial length of the firing pin.
  • the chisel hammer 11 shown in FIGS. 1 and 1A has a housing 12 in which an electropneumatic impact mechanism 21 and a motor / gear unit 14 are arranged.
  • the percussion mechanism 21 has an excitation piston 23 which is guided back and forth along the striking axis 22 by means of an eccentric device 13 actuated by the motor / gear unit 14 in a guide tube 17.
  • percussion piston 25 is also displaced in reciprocating motion, which acts with an exposed and outside the striking axis 22 arranged contact point 27 via a mating contact point 28 on the firing pin 26 on this ,
  • the firing pin 26 transmits the impulse generated by the striking mechanism 21 to the insertion end 16 of the tool.
  • the guide tube 17 has for venting the air cushion between the excitation piston 23 and the percussion piston 25 ventilation openings 18.
  • the contact point 27 is arranged outside the striking axis 22.
  • the contact point 27 is arranged at a distance D from the impact axis 22 which corresponds to 0.02 times the axial length L of the firing pin 26. If the firing pin 26 has an axial length L of, for example, 100 mm, the distance D is thus 2 mm.
  • the chisel hammer 31 shown in FIG. 3 is substantially analogous to the chisel hammer 11 and differs only in the design of the percussion mechanism 41.
  • the percussion mechanism 41 has a percussion piston 45, which is influenced by the excitation piston 43 and serves as percussion means 44 , Wherein this on the firing pin 46 side facing a contact point 47 which acts via a mating contact point 48 on the firing pin 46.
  • the contact point 47 is exposed and arranged outside the striking axis 42.
  • the contact point 47 is arranged at a distance d from the impact axis 42, which corresponds to 0.03 times the axial length l of the firing pin 46. If the firing pin 46 has an axial length l of, for example, 80 mm, the distance d is thus 2.4 mm.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
EP06112584A 2005-04-25 2006-04-13 Marteau perforateur ou marteau-burineur Active EP1716979B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005000042A DE102005000042A1 (de) 2005-04-25 2005-04-25 Bohr-oder Meisselhammer

Publications (2)

Publication Number Publication Date
EP1716979A1 true EP1716979A1 (fr) 2006-11-02
EP1716979B1 EP1716979B1 (fr) 2011-09-28

Family

ID=36648697

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06112584A Active EP1716979B1 (fr) 2005-04-25 2006-04-13 Marteau perforateur ou marteau-burineur

Country Status (5)

Country Link
US (1) US20060237206A1 (fr)
EP (1) EP1716979B1 (fr)
JP (1) JP4865395B2 (fr)
CN (1) CN1853865B (fr)
DE (1) DE102005000042A1 (fr)

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005062777A1 (de) * 2005-12-28 2007-07-05 Robert Bosch Gmbh Schlagbolzen für ein Schlagwerk
GB201112829D0 (en) 2011-07-26 2011-09-07 Black & Decker Inc Hammer
US8657028B2 (en) * 2011-08-31 2014-02-25 Raymond Stoner Impact hammer
CN102756358B (zh) * 2012-07-25 2014-12-10 贵州科学院 一种可缓冲的变频冲击式多功能电动工具
EP2857149A1 (fr) * 2013-10-03 2015-04-08 HILTI Aktiengesellschaft Machine-outil manuelle
EP2871030A1 (fr) 2013-11-06 2015-05-13 HILTI Aktiengesellschaft Machine-outil manuelle
EP2918376A1 (fr) * 2014-03-12 2015-09-16 HILTI Aktiengesellschaft Machine-outil portative de burinage
GB201421576D0 (en) 2014-12-04 2015-01-21 Black & Decker Inc Drill
GB201421577D0 (en) * 2014-12-04 2015-01-21 Black & Decker Inc Drill
WO2019079560A1 (fr) 2017-10-20 2019-04-25 Milwaukee Electric Tool Corporation Outil à percussion
WO2019147919A1 (fr) 2018-01-26 2019-08-01 Milwaukee Electric Tool Corporation Outil à percussion
JP7222703B2 (ja) * 2018-04-11 2023-02-15 株式会社マキタ 打撃工具
US10710229B2 (en) 2018-04-18 2020-07-14 Raymond Stoner Impact hammer
US11583987B2 (en) 2018-04-18 2023-02-21 Raymond Stoner Impact hammer system
EP3670097A1 (fr) * 2018-12-21 2020-06-24 Hilti Aktiengesellschaft Machine-outil portative
EP3670096A1 (fr) 2018-12-21 2020-06-24 Hilti Aktiengesellschaft Machine-outil portative
CN110340852B (zh) * 2019-08-13 2024-02-27 油特机械工具（大连）有限公司 一种高精度长寿命充电式冲点枪
JP7412135B2 (ja) * 2019-11-05 2024-01-12 株式会社マキタ 打撃工具
CN114817866B (zh) * 2022-07-01 2022-09-06 南通佰瑞利电动工具有限公司 基于主轴偏置负载现场分析的电钻功率计算方法及系统

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE415037A (fr) *
BE383061A (fr) *
US2260070A (en) * 1941-01-09 1941-10-21 Black & Decker Mfg Co Portable hammer
US2730073A (en) * 1953-06-23 1956-01-10 Mechanical Res Corp Percussion tools
DE1283769B (de) * 1963-05-15 1968-11-21 Impex Essen Vertrieb Schlaghammer
DE3121616A1 (de) * 1981-05-30 1982-12-23 Robert Bosch Gmbh, 7000 Stuttgart Bohrhammer
DE3526162A1 (de) * 1985-07-22 1987-01-22 Black & Decker Inc Bohrhammer sowie bohrhammerwerkzeug

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1911814A (en) * 1931-04-29 1933-05-30 Black & Decker Mfg Co Portable power driven percussive tool
US3032998A (en) * 1961-05-05 1962-05-08 Black & Decker Mfg Co Ram catcher for piston-ram assembly
US3973633A (en) * 1972-06-30 1976-08-10 Atlas Copco Aktiebolag Hammer device
US3952813A (en) * 1975-02-07 1976-04-27 Nikolai Prokhorovich Chepurnoi Percussive device for driving holes in soil
US4290492A (en) * 1979-01-31 1981-09-22 Black & Decker Inc. Idling and air replenishing system for a reciprocating hammer mechanism
SU1052627A1 (ru) * 1979-05-14 1983-11-07 Институт Горного Дела Со Ан Ссср Машина ударного действи
ES2026199T3 (es) * 1986-12-17 1992-04-16 Hilti Aktiengesellschaft Aparato manual.
SE8900947D0 (sv) * 1989-03-16 1989-03-16 Atlas Copco Ab Slagverktyg
DE4135240A1 (de) * 1991-10-25 1993-04-29 Bosch Gmbh Robert Bohrhammer
DE19706671A1 (de) * 1997-02-20 1998-08-27 Scintilla Ag Handwerkzeugmaschine
CN2652605Y (zh) * 2003-09-02 2004-11-03 林瑞兴 冲击切断机

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE415037A (fr) *
BE383061A (fr) *
US2260070A (en) * 1941-01-09 1941-10-21 Black & Decker Mfg Co Portable hammer
US2730073A (en) * 1953-06-23 1956-01-10 Mechanical Res Corp Percussion tools
DE1283769B (de) * 1963-05-15 1968-11-21 Impex Essen Vertrieb Schlaghammer
DE3121616A1 (de) * 1981-05-30 1982-12-23 Robert Bosch Gmbh, 7000 Stuttgart Bohrhammer
DE3526162A1 (de) * 1985-07-22 1987-01-22 Black & Decker Inc Bohrhammer sowie bohrhammerwerkzeug

Also Published As

Publication number Publication date
CN1853865B (zh) 2010-09-29
CN1853865A (zh) 2006-11-01
US20060237206A1 (en) 2006-10-26
JP4865395B2 (ja) 2012-02-01
JP2006305722A (ja) 2006-11-09
DE102005000042A1 (de) 2006-10-26
EP1716979B1 (fr) 2011-09-28

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