EP2452782B1 - Outil à main - Google Patents

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Publication number
EP2452782B1
EP2452782B1 EP11185181.2A EP11185181A EP2452782B1 EP 2452782 B1 EP2452782 B1 EP 2452782B1 EP 11185181 A EP11185181 A EP 11185181A EP 2452782 B1 EP2452782 B1 EP 2452782B1
Authority
EP
European Patent Office
Prior art keywords
absorbers
hand
machine tool
held machine
working axis
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.)
Active
Application number
EP11185181.2A
Other languages
German (de)
English (en)
Other versions
EP2452782A3 (fr
EP2452782A2 (fr
Inventor
Oliver Ohlendorf
Jörg Martin
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 EP2452782A2 publication Critical patent/EP2452782A2/fr
Publication of EP2452782A3 publication Critical patent/EP2452782A3/fr
Application granted granted Critical
Publication of EP2452782B1 publication Critical patent/EP2452782B1/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
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/006—Vibration damping means
    • 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
    • B25D2211/06—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
    • 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
    • B25D2250/275—Tools having at least two similar components
    • 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
    • B25D2250/371—Use of springs
    • B25D2250/381—Leaf springs

Definitions

  • the present invention relates to a hand tool with an absorber.
  • Examples are from the EP2072191A1 or US2010038105A1 known.
  • a hand tool has a linear drive for moving a tool along a working axis, e.g. a motorized pneumatic striking mechanism.
  • At least two dampers are provided in the hand tool for damping vibrations along the working axis.
  • a resonant excitation of an oscillation of the first damper along the working axis takes place at a first resonance frequency, which differs from a second resonance frequency of the second damper for the oscillation along the working axis.
  • the two resonance frequencies differ in a range from 2% to 5%, i.e. the first frequency is 1.02 to 1.05 times greater than the second resonance frequency.
  • each of the two absorbers has a pendulum arm and a mass body.
  • the mass body is resiliently attached to a housing of the handheld power tool by means of the pendulum arm.
  • the end of the pendulum arm that is distant from the mass body forms a bearing point around which the mass body executes a torsional vibration, guided by the pendulum arm.
  • the deflection preferably remains low, e.g. less than 30 degrees around the bearing point, whereby the movement of the mass body is considered approximately as along the working axis.
  • the pendulum arm or the bearing is designed to be very stiff against deflection out of the plane of rotation, which results in very high resonance frequencies. These high resonance frequencies should be at least an order of magnitude or 10 times higher than the resonance frequencies for excitation along the working axis in order not to be excitable.
  • the resonance frequencies of the two absorbers can be adjusted by the length of the pendulum arms, which can differ in a range from 4% to 10%.
  • the length denotes the distance from the center of gravity of the mass body to that Bearing point of the pendulum arm on the housing.
  • the mass of the mass bodies can differ by 4% to 10%.
  • the pendulum arm of a first of the two absorbers is arranged parallel to a pendulum arm of a second of the two absorbers.
  • the pendulum arms can be inclined at least 70 degrees to the working axis.
  • the pendulum arms can be designed as a leaf spring.
  • the leaf springs can be connected by a web at an end remote from the mass bodies.
  • the two leaf springs are manufactured as a stamped part.
  • the mass body can be attached to the pendulum arm.
  • One embodiment provides that a periodicity with which the linear drive moves the tool along the working axis lies between the resonance frequencies of the two absorbers.
  • the tool typically becomes very anharmonic, i.e. clearly not sinusoidal. Therefore, the term periodicity or repetition rate seems more appropriate to indicate how often the tool moves back and forth in a time standard.
  • the periodicity is measured as a frequency in Hertz. If a frequency is used in the application for the description of an anharmonic movement, this denotes the basic frequency.
  • Fig. 1 shows schematically a hammer drill 1.
  • the hammer drill 1 has a tool holder 2 , in which a drill bit 3 can be used as a tool.
  • a motor 4 which drives an impact mechanism 5 and an output shaft 6, forms a primary drive of the hammer drill 1 .
  • a user can guide the hammer drill 1 by means of a handle 7 and put the hammer drill 1 into operation by means of a system switch 8 .
  • the hammer drill 1 continuously rotates the drill bit 3 about a working axis 9 and can thereby strike the drill bit 3 along the working axis 9 into an underground.
  • the striking mechanism 5 is, for example, a pneumatic striking mechanism 5.
  • An exciter 10 and a striker 11 are movably guided in the striking mechanism 5 along the working axis 9 .
  • the exciter 10 is coupled to the motor 4 via an eccentric 12 or a wobble finger and is forced to perform a periodic, linear movement.
  • An air spring formed by a pneumatic chamber 13 between the exciter 10 and the striker 11 couples a movement of the striker 11 to the movement of the exciter 10 .
  • the striker 11 can strike directly onto a rear end of the drill bit 3 or indirectly transfer part of its impulse to the drill bit 3 via an essentially stationary intermediate striker 14 .
  • the striking mechanism 5 and preferably the further drive components are arranged within a machine housing 15 .
  • a first damper 20 and a second damper 21 are arranged within the machine housing 15 .
  • the first damper 20 hides the second damper 21.
  • the section in the plane II-II through the two damper 20 , 21 is in Fig. 2 shown.
  • the first absorber 20 has a first mass body 22 , which is connected via a leaf spring 23 to a rigid bearing point 24 on the housing 15 .
  • the leaf spring 23 In the rest position, the leaf spring 23 is arranged at an angle 25 of at least 70 degrees to the working axis 9 .
  • a movement of the machine housing 15 along the working axis 9 can stimulate the mass body 22 to perform the same movement along the working axis 9 .
  • the mass body 22 is guided by the leaf spring 23 , the mass body 22 follows a curved path 26.
  • the deflections of the mass body 22 are small compared to a length 27 of the leaf spring 23 , as a result of which the movement can be assumed to be approximately parallel to the working axis 9 .
  • the length 27 of the leaf spring 23 is measured from the attachment 24 to the center of gravity of the first mass body 22 .
  • the leaf spring 23 counteracts a deflection of the mass body 22 from its rest position by a restoring force.
  • the restoring spring force, the length 27 of the leaf spring 23 and the mass of the mass body 22 determine a resonance frequency of the first damper 20 .
  • the leaf spring 23 has a lower rigidity along the working axis 9 compared to the directions perpendicular to the working axis 9. An excitation of the leaf spring 23 perpendicular to the working axis 9 is therefore only possible at very high frequencies.
  • the second damper 21 is constructed essentially the same as the first damper 20 .
  • a second mass body 28 is connected to the machine housing 15 via a second leaf spring 29 .
  • the second leaf spring 29 is preferably arranged parallel to the first leaf spring 23 and also, in the rest position, inclined by at least 70 degrees to the working axis 9 .
  • the two leaf springs 22 , 29 preferably have the same spring constant and thickness, whereas a length 30 of the second leaf spring 29 is 4% to 10% longer than the length 27 of the first leaf spring 22.
  • a mass of the second mass body 28 is approximately equal to the mass of the first mass body 22.
  • the different lengths 30 , 29 bring about a 2% to 5% lower resonance frequency of the second absorber 21.
  • the mass bodies 22 , 28 have a mass that is 4% to 10% different.
  • the leaf springs 22 , 29 can be produced as a stamped sheet.
  • the two leaf springs 22 , 29 can be connected via a bridge 31 .
  • Fig. 3 shows the behavior of the two absorbers 20 , 21 for different excitation frequencies f, the deflection is plotted on the ⁇ -axis normalized to the maximum deflection (amplitude) of the mass bodies 22 , 28 along the working axis 9 .
  • Curve 32 indicates the excitation spectrum for the first absorber 20
  • curve 33 the excitation spectrum for the second absorber 21 .
  • the two absorbers 20 , 21 are out of tune with each other.
  • the detuning of the resonance frequency 34 of the first damper 20 is greater than the resonance frequency 35 of the second damper 21. Excitation of a damper with frequencies greater than its resonance frequency can lead to an oscillation of the damper in the hand tool 1 and causes vibrations to be eradicated instead of being desired Increase the vibrations. This actually speaks against the use of a second damper with a different frequency for the damping of vibrations along the working axis 9.
  • the two dampers 20 , 21 are only slightly out of tune with one another, they will probably couple to one another and the low-frequency damper 21 does not yet build up when the excitation frequency f by the linear drive 5 lies between the resonance frequencies 35 , 34 of the two absorbers 20 , 21 .
  • the resonance frequency 34 of the first damper 20 should lie within a frequency band 36 within which the excitation spectrum 32 of the second damper 21 drops to no more than a quarter (hatched area), preferably no more than half of the maximum amplitude.
  • the two absorbers 20 , 21 then couple strongly to one another. Overall, there is a broader response for the overall system from the two absorbers 20 , 21 .
  • the coupling of the two absorbers 20 , 21 can be increased by the elastic bridge 31 between the leaf springs 29 , 22 .
  • the resonance frequencies 34 , 35 are preferably set via the pendulum arms 23 , 29 and the mass bodies 22 , 28 so that a periodicity of the linear drive 5 lies between the resonance frequencies 34 , 35 .
  • the absorbers 20 , 21 can also be used in a jigsaw or a saber saw.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)

Claims (10)

  1. Machine-outil manuelle comportant un entraînement linéaire pour déplacer un outil le long d'un axe de travail (9) et deux amortisseurs (20, 21) dont les fréquences de résonance sont différentes pour un mouvement le long de l'axe de travail (9), dans laquelle la fréquence de résonance du premier des deux amortisseurs (20) se situe dans une bande de fréquences à l'intérieur de laquelle le second amortisseur excité (21) parmi les deux amortisseurs vibre avec une déviation qui correspond au moins à un quart d'une déviation pendant l'excitation de résonance du second amortisseur (21) .
  2. Machine-outil manuelle selon la revendication 1, caractérisée en ce que les fréquences de résonance des amortisseurs (20, 21) diffèrent d'au moins 2 %.
  3. Machine-outil manuelle selon la revendication 1 ou 2, caractérisée en ce que chacun des deux amortisseurs (20, 21) comporte respectivement un bras pendulaire (23, 29) et une masselotte (22, 28) qui est fixée élastiquement à un boîtier (15) de la machine-outil manuelle (1) au moyen du bras pendulaire (23, 29).
  4. Machine-outil manuelle selon la revendication 3, caractérisée en ce qu'une longueur (27, 30) des bras pendulaires (23, 29) et/ou une masse des masselottes (28, 29) diffère dans une plage de 4 % à 10 %.
  5. Machine-outil manuelle selon la revendication 3 ou 4, caractérisée en ce que le bras pendulaire (23, 29) d'un premier des deux amortisseurs (20, 21) est agencé parallèlement au bras pendulaire (29, 23) d'un second des deux amortisseurs (21, 20).
  6. Machine-outil manuelle selon la revendication 3, caractérisée en ce que les bras pendulaires (23, 29) sont agencés de manière inclinée d'au moins 70 degrés par rapport à l'axe de travail.
  7. Machine-outil manuelle selon la revendication 3, caractérisée en ce que les bras pendulaires (23, 29) sont formés comme des ressorts à lame.
  8. Machine-outil manuelle selon la revendication 7, caractérisée en ce que les ressorts à lame sont reliés par une nervure au niveau d'une extrémité éloignée des masselottes (22, 28).
  9. Machine-outil manuelle selon l'une des revendications précédentes, caractérisée en ce qu'une fréquence de résonance pour une excitation des deux amortisseurs (20, 21) pendant un mouvement perpendiculairement à l'axe de travail est supérieure d'au moins un ordre de grandeur à la fréquence de résonance pour le mouvement le long de l'axe de travail.
  10. Machine-outil manuelle selon l'une des revendications précédentes, caractérisée en ce qu'une périodicité à laquelle l'entraînement linéaire (5) déplace l'outil le long de l'axe de travail (9) est comprise entre les fréquences de résonance (34, 35) des deux amortisseurs (20, 21).
EP11185181.2A 2010-11-12 2011-10-14 Outil à main Active EP2452782B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102010043810A DE102010043810A1 (de) 2010-11-12 2010-11-12 Handwerkzeugmaschine

Publications (3)

Publication Number Publication Date
EP2452782A2 EP2452782A2 (fr) 2012-05-16
EP2452782A3 EP2452782A3 (fr) 2018-02-28
EP2452782B1 true EP2452782B1 (fr) 2019-12-18

Family

ID=44785646

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11185181.2A Active EP2452782B1 (fr) 2010-11-12 2011-10-14 Outil à main

Country Status (3)

Country Link
US (1) US20120125649A1 (fr)
EP (1) EP2452782B1 (fr)
DE (1) DE102010043810A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014069293A (ja) * 2012-09-28 2014-04-21 Hitachi Koki Co Ltd 打撃工具
EP2848370A1 (fr) * 2013-09-12 2015-03-18 HILTI Aktiengesellschaft Machine-outil manuelle
EP2886261A1 (fr) * 2013-12-18 2015-06-24 HILTI Aktiengesellschaft Machine-outil manuelle
CN106457543B (zh) * 2014-04-30 2019-11-19 工机控股株式会社 作业工具
EP3028818A1 (fr) * 2014-12-03 2016-06-08 HILTI Aktiengesellschaft Machine-outil portative

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS54127080A (en) * 1978-03-25 1979-10-02 Makoto Nandate Vibration isolation device in handle of machine in which vibration is formed
EP1404493B1 (fr) * 2001-04-11 2007-02-14 Robert Bosch Gmbh Machine-outil portative presentant une poignee avec un systeme d'amortissement des vibrations
JP4793755B2 (ja) * 2006-03-07 2011-10-12 日立工機株式会社 電動工具
EP2142342B1 (fr) * 2007-05-01 2015-06-24 Hitachi Koki CO., LTD. Outil à mouvement alternatif
US7806201B2 (en) * 2007-07-24 2010-10-05 Makita Corporation Power tool with dynamic vibration damping
DE102007055843A1 (de) * 2007-12-17 2009-06-25 Hilti Aktiengesellschaft Handwerkzeugmaschine mit Schwingungsausgleicher
DE102007060636A1 (de) * 2007-12-17 2009-06-18 Robert Bosch Gmbh Elektrohandwerkzeug, insbesondere ein Bohr- und/oder Meißelhammer, mit einer Tilgereinheit
DE102008000625A1 (de) * 2008-03-12 2009-09-17 Robert Bosch Gmbh Handwerkzeugmaschine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP2452782A3 (fr) 2018-02-28
US20120125649A1 (en) 2012-05-24
DE102010043810A1 (de) 2012-05-16
EP2452782A2 (fr) 2012-05-16

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