EP2425937A1 - Machine-outil à main - Google Patents

Machine-outil à main Download PDF

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Publication number
EP2425937A1
EP2425937A1 EP11176970A EP11176970A EP2425937A1 EP 2425937 A1 EP2425937 A1 EP 2425937A1 EP 11176970 A EP11176970 A EP 11176970A EP 11176970 A EP11176970 A EP 11176970A EP 2425937 A1 EP2425937 A1 EP 2425937A1
Authority
EP
European Patent Office
Prior art keywords
spring
mass body
hand tool
basic position
springs
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
EP11176970A
Other languages
German (de)
English (en)
Other versions
EP2425937B1 (fr
Inventor
Michael Wierer
Fabian Martin
Adrian Scherrer
Josef Althaus
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 EP2425937A1 publication Critical patent/EP2425937A1/fr
Application granted granted Critical
Publication of EP2425937B1 publication Critical patent/EP2425937B1/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
    • B25D17/04—Handles; Handle mountings
    • B25D17/043—Handles resiliently mounted relative to the hammer housing
    • 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
    • B25D17/24—Damping the reaction force
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/003—Crossed drill and motor spindles
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
    • B25D2211/06—Means for driving the impulse member
    • B25D2211/068—Crank-actuated impulse-driving mechanisms
    • 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
    • B25D2217/0073—Arrangements for damping of the reaction force
    • B25D2217/0076—Arrangements for damping of the reaction force by use of counterweights
    • B25D2217/0092—Arrangements for damping of the reaction force by use of counterweights being spring-mounted

Definitions

  • the hand tool e.g. a hand-held power tool with a pneumatic percussion mechanism, periodically gives the user a setback. Their amplitude can be attenuated by the absorber. An asymmetrically constructed Tilger can cause a higher damping effect in the power tool.
  • the spring stiffness may have a discontinuity or very strong change relative to the home position. The discontinuity results in a highly non-harmonic motion of the mass body and non-harmonic forces, which may be more appropriate to dampen the engine case.
  • the first spring stiffness is between five and ten times the second spring stiffness.
  • the ratio of the spring stiffnesses can be used to adjust the damping of the absorber to the non-return behavior of the power tool. The higher the ratio, the shorter and stronger the mass body is accelerated by the stiffer side.
  • An embodiment provides that the mass body in the second direction deflected from the basic position of at least one spring force-free and in the first direction deflected from the basic position of the at least one spring is subjected to force.
  • An embodiment provides that the mass body rests in the basic position on the spring. Rubbers with friction prove to be inefficient for use in hand tool machines. The coupling and decoupling of the spring and the resulting losses should be largely minimized. In the basic position, the other forces of the spring device cancel.
  • the mass body may be arranged in the basic position between two prestressed springs. An embodiment provides that the two prestressed springs are firmly connected to the mass body. Due to the fixed connection results in low losses in the springs due to plastic deformation or due to friction.
  • Fig. 1 shows as an embodiment a hammer drill 1 bz.
  • the hammer drill 1 bz has a tool holder 2bz for receiving a drill bit 3bz.
  • a striking mechanism 4bz of the hammer drill 1 bz strikes periodically along a working axis 5bz on the drill bit 3bz inserted in the tool holder 2bz and thereby drives it into a Underground.
  • a rotary drive 6bz can meanwhile rotate the drill bit 3bz about the working axis 5bz .
  • the striking mechanism 4bz and the rotary drive 6bz can be driven by a common motor 7bz, eg an electric motor.
  • a machine housing 8bz surrounds the striking mechanism 4bz, the rotary drive 6bz and the possibly common motor 7bz.
  • the Schlagtechnik 4bz is for example a pneumatic percussion.
  • An exciter 9bz and a club 10bz are movably guided in the pneumatic percussion mechanism 4bz along the working axis 5bz .
  • the exciter 9bz is coupled via an eccentric 11bz or a wobble finger to the motor 7bz and forced to a periodic, linear movement.
  • An air spring formed by a pneumatic chamber 12bz between exciter 9bz and racket 10bz couples a movement of the racket 10bz to the movement of the exciter 9bz .
  • the beater 10bz can strike directly on a rear end of the drill bit 3bz or indirectly transfer part of its momentum to the drill bit 3bz via a substantially stationary beater 13bz .
  • the user can perform the hammer drill 1 bz by hand by means of a handle 16bz .
  • the handle 16bz is attached to a side facing away from the tool holder 2bz side of the machine housing 8bz .
  • a longitudinal axis 17bz of the handle 16bz extends obliquely or perpendicular to the working axis 5bz.
  • the hammer drill 1 bz is, for example mirror-symmetrical to a plane of symmetry (corresponds to the plane of the drawing), which is spanned by the working axis 5bz and the longitudinal axis 17bz of the handle 16bz .
  • An axis perpendicular to the plane of symmetry is hereinafter referred to as the x-axis.
  • the y-axis is perpendicular to the x-axis and to the working axis 5bz.
  • the periodically operating impact mechanism 4bz causes vibrations in the engine case 8bz.
  • Spring suspensions 20Cz, 21bz of the handle 16bz on the machine housing 8bz partially suppress transmission of the vibrations to the handle 16bz to reduce the physiological stresses on the user.
  • the absorber 30Cz has a mass body 31 bz, which is connected by means of a spring device 32bz to the machine housing 8bz .
  • the oscillating machine housing 8bz stimulates the mass body 31 bz of the absorber 30Cz to resonate.
  • the system of mass body 31bz and a spring means 32bz is tuned to a natural frequency which is slightly larger than the excitation frequency through the machine housing 8bz, ie the repetition rate of the impact mechanism 4bz .
  • the absorber 30Cz can not quite follow the vibration of the machine housing 8bz and stabilizes in an antiphase oscillation.
  • the deviation of the natural frequency to the excitation frequency is preferably low, z. B. less than 10%, whereby an efficient energy transfer between the machine housing 8bz and absorber 30Cz is achieved.
  • Fig. 2 shows in detail an embodiment of the absorber 30Cz.
  • the absorber 30Cz has a housing 33bz, in which the mass body 31 bz is mounted longitudinally to a vibration axis 34bz .
  • An exemplary bearing 35bz includes round bars 36bz which are mounted in parallel to the vibration axis 34bz in the housing 33bz .
  • the mass body 31 bz has longitudinal bore 37bz or longitudinal grooves extending through the round rods 36bz .
  • the bearing 35bz is preferably low friction.
  • Other embodiments of linear bearings, eg with rolling bodies can also be used.
  • the mass body 31 bz can from a basic position 38bz (in Fig. 2 shown) along the vibration axis 34bz 30Cz be moved out in a first direction 39bz to a first end of the damper 40bz 30Cz and along the oscillation axis 34bz in an opposite, second direction 41 bz to a second end of the damper 42bz.
  • the spring device 32bz causes a restoring force on the mass body 31bz, as soon as it is deflected from the basic position 38bz .
  • the spring device 32bz is constructed asymmetrically to the basic position 38bz .
  • the exemplary spring means 32bz has first springs 44bz, second springs 45bz and a third spring 46bz.
  • the first springs 44bz are fastened to the first end of the housing 40bz 33bz and the mass body 31 bz, z. B. by clamping elements 47bz, 48bz.
  • the first springs 44bz push the mass body 31 bz deflected from the basic position 38bz in the second direction 41 bz.
  • the second springs 45bz are attached to the second end 42bz of the housing 33bz and to the mass body 31 bz .
  • the second springs 45bz of the mass body 31 bz is deflected from the basic position 38bz in the first direction 39bz kraftbeetzschlagt.
  • the first springs 44bz and second springs 45bz may be of the same design, eg with the same length and the same spring rigidity .
  • the first springs 44bz and second springs 45bz may be biased when the mass body 31 bz is in the home position 38bz .
  • the first springs 44bz and second springs 45bz may also be biased when the mass body 31 bz are deflected maximally in one or the other direction 39bz, 41 bz .
  • a load change of pressure load on tensile load of the springs 44bz, 45bz can be avoided.
  • the third spring 46bz is arranged only on one side of the mass body 31 bz, by way of example between the first end 40bz of the housing 33bz and the mass body 31 bz.
  • the third spring 46bz is fixedly connected to the housing 33bz, but only in the mass body 31 bz in whose basic position 38bz created.
  • the third spring 46bz is compressed.
  • the third spring 46bz detaches itself from the mass body 31 as soon as it exceeds the basic position 38bz .
  • the third spring 46bz fixedly connected to the mass body 31 bz and detaches from a seat 49bz on the housing 33bz.
  • the length of the third spring 46bz is equal to the distance of the mass body 31 bz selected to the seat 49bz .
  • the third spring 46bz is without bias when the mass body 31 bz is in the home position 38bz .
  • the spring stiffness of the spring means 32bz on the first side 50bz of the mass body 31 bz, ie in the first direction 39bz, can be five to ten times larger than the spring stiffness of the spring device 32bz on the second side 51 bz.
  • the third spring 46bz having three to eight times stiffness may be selected as the same first and second springs 45bz, 42bz .
  • the springs 44bz, 45bz, 46bz are, for example, coil springs made of steel.
  • the first springs 44bz and the second springs 45bz may be arranged coaxially with the round bars 36bz .
  • the swing axis 34bz is inclined parallel or at an angle of less than 5 degrees to the working axis 5bz of the portable power tool 1bz .
  • the spring device 32bz has a bending spring 60Cz, for example, leaf spring, which is aligned perpendicular to the swing axis 34bz .
  • the bending spring 60Cz is fixed with one end 61 bz to a seat 62bz in the housing 33bz of the damper 63bz .
  • At the other end 64bz of the mass body 31 bz is attached.
  • the mass body 31 bz oscillates along the swing axis 34bz, bending the bending spring 60Cz along its longitudinal extent .
  • a basic position 38bz of the mass body 31 bz results in a relaxed, unbent bending spring 60Cz.
  • a helical spring 65bz is arranged parallel to the oscillating axis 34bz on one side to the mass body 31 bz .
  • the coil spring 65bz touches the mass body 31 bz when it is in the normal position .
  • the coil spring 65bz In a deflection of the mass body 31 bz in the first direction 39bz , the coil spring 65bz is compressed.
  • On the mass body 31 bz act the restoring forces of the bending spring 60Cz and the coil spring 65bz.
  • a deflection of the mass body 31 bz in the opposite second direction 41 bz dissolves the mass body 31 bz of the coil spring 65bz. It acts only the restoring force of the bending spring 60Cz on the mass body 31 bz.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
EP20110176970 2010-09-02 2011-08-09 Machine-outil à main Active EP2425937B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201010040173 DE102010040173A1 (de) 2010-09-02 2010-09-02 Handwerkzeugmaschine

Publications (2)

Publication Number Publication Date
EP2425937A1 true EP2425937A1 (fr) 2012-03-07
EP2425937B1 EP2425937B1 (fr) 2015-02-25

Family

ID=44651104

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20110176970 Active EP2425937B1 (fr) 2010-09-02 2011-08-09 Machine-outil à main

Country Status (5)

Country Link
US (1) US8985236B2 (fr)
EP (1) EP2425937B1 (fr)
CN (1) CN102380854B (fr)
DE (1) DE102010040173A1 (fr)
ES (1) ES2532738T3 (fr)

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9849577B2 (en) 2012-02-03 2017-12-26 Milwaukee Electric Tool Corporation Rotary hammer
WO2013116680A1 (fr) 2012-02-03 2013-08-08 Milwaukee Electric Tool Corporation Marteau rotatif
JP5870888B2 (ja) * 2012-09-28 2016-03-01 日立工機株式会社 打撃工具
RU2620399C2 (ru) * 2012-03-22 2017-05-25 Хитачи Коки Ко., Лтд. Импульсно-силовая ручная машина
US10232500B2 (en) 2012-12-17 2019-03-19 Swerea Ivf Ab Impact machine
JP6271577B2 (ja) * 2012-12-17 2018-01-31 スウェレア・アイブイエフ・エービーＳｗｅｒｅａ ＩＶＦ ＡＢ 衝撃マシン
JP6085225B2 (ja) * 2013-06-27 2017-02-22 株式会社マキタ ネジ締め電動工具
EP2848370A1 (fr) * 2013-09-12 2015-03-18 HILTI Aktiengesellschaft Machine-outil manuelle
JP6385069B2 (ja) * 2014-02-24 2018-09-05 住友重機械工業株式会社 ショベル
WO2015193284A1 (fr) * 2014-06-16 2015-12-23 Swerea Ivf Ab Machine d'impact
JP6863704B2 (ja) 2016-10-07 2021-04-21 株式会社マキタ 打撃工具
US10814468B2 (en) 2017-10-20 2020-10-27 Milwaukee Electric Tool Corporation Percussion tool
EP4349534A2 (fr) 2018-01-26 2024-04-10 Milwaukee Electric Tool Corporation Outil à percussion
EP3626398A1 (fr) 2018-09-19 2020-03-25 Hilti Aktiengesellschaft Amortisseur biharmonique à contrainte
US11845168B2 (en) * 2019-11-01 2023-12-19 Makita Corporation Reciprocating tool
JP2022119301A (ja) * 2021-02-04 2022-08-17 株式会社マキタ 打撃工具
JP2022128006A (ja) * 2021-02-22 2022-09-01 株式会社マキタ 打撃工具
US11642769B2 (en) * 2021-02-22 2023-05-09 Makita Corporation Power tool having a hammer mechanism

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2018939A2 (fr) * 2007-07-24 2009-01-28 Makita Corporation Outil électrique avec amortisseur de vibration
DE102007055843A1 (de) * 2007-12-17 2009-06-25 Hilti Aktiengesellschaft Handwerkzeugmaschine mit Schwingungsausgleicher
EP2143530A1 (fr) * 2008-07-07 2010-01-13 Makita Corporation Outil électrique
EP2159008A2 (fr) * 2008-08-29 2010-03-03 Makita Corporation Outil d'impact

Family Cites Families (16)

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DE815179C (de) * 1949-11-17 1951-10-01 Franz Dr-Ing Bollenrath Drucklufthammer mit Massenausgleich
JPS594264B2 (ja) * 1980-06-27 1984-01-28 南舘 誠 振動抑制型のハンドル装置
DE10036078B4 (de) * 2000-07-25 2007-04-05 Robert Bosch Gmbh Handwerkzeugmaschine mit einem Handgriff und einer Isoliervorrichtung
EP1415768A1 (fr) * 2002-10-31 2004-05-06 Atlas Copco Electric Tools GmbH Amortisseur d'oscillations
AU2003244065A1 (en) * 2003-06-09 2005-01-04 Tan-Cheng Huang Shock absorber structure for the front fork of a vehicle
US7604071B2 (en) * 2004-04-30 2009-10-20 Makita Corporation Power tool with vibration reducing means
DE102004021905B3 (de) * 2004-05-04 2005-11-03 Stefan Windschiegl Schwingungsdämpfer für Stemmlanzen und Druckluftwerkzeuge allgemein
JP4647957B2 (ja) * 2004-08-27 2011-03-09 株式会社マキタ 作業工具
GB2429675A (en) * 2005-06-23 2007-03-07 Black & Decker Inc Vibration dampening mechanism
DE102006000375A1 (de) * 2006-07-27 2008-01-31 Hilti Ag Handwerkzeuggerät mit Entkoppelungsanordnung
DE102006000374A1 (de) * 2006-07-27 2008-01-31 Hilti Ag Handwerkzeuggerät mit Entkopplungsanordnung
DE102007000059A1 (de) * 2007-01-31 2008-09-18 Hilti Aktiengesellschaft Handwerkzeugmaschine mit Schwingungstilger
DE102007000093A1 (de) * 2007-02-15 2008-08-21 Hilti Ag Handwerkzeuggerät
DE102007042721A1 (de) * 2007-09-07 2009-03-12 Robert Bosch Gmbh Handwerkzeugmaschine mit einem durch ein Ausgleichsmittel schwingungsgedämpften Handgriff
DE102007055792A1 (de) * 2007-12-13 2009-06-18 Hilti Aktiengesellschaft Elektrohandwerkzeugmaschine mit Schwingungsausgleicher
DE102007060636A1 (de) * 2007-12-17 2009-06-18 Robert Bosch Gmbh Elektrohandwerkzeug, insbesondere ein Bohr- und/oder Meißelhammer, mit einer Tilgereinheit

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2018939A2 (fr) * 2007-07-24 2009-01-28 Makita Corporation Outil électrique avec amortisseur de vibration
DE102007055843A1 (de) * 2007-12-17 2009-06-25 Hilti Aktiengesellschaft Handwerkzeugmaschine mit Schwingungsausgleicher
EP2143530A1 (fr) * 2008-07-07 2010-01-13 Makita Corporation Outil électrique
EP2159008A2 (fr) * 2008-08-29 2010-03-03 Makita Corporation Outil d'impact

Also Published As

Publication number Publication date
CN102380854B (zh) 2015-09-16
EP2425937B1 (fr) 2015-02-25
US8985236B2 (en) 2015-03-24
US20120055689A1 (en) 2012-03-08
ES2532738T3 (es) 2015-03-31
DE102010040173A1 (de) 2012-03-08
CN102380854A (zh) 2012-03-21

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