EP1787761B1 - Perçeuse motorisée à percussion - Google Patents

Perçeuse motorisée à percussion Download PDF

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Publication number
EP1787761B1
EP1787761B1 EP05024979A EP05024979A EP1787761B1 EP 1787761 B1 EP1787761 B1 EP 1787761B1 EP 05024979 A EP05024979 A EP 05024979A EP 05024979 A EP05024979 A EP 05024979A EP 1787761 B1 EP1787761 B1 EP 1787761B1
Authority
EP
European Patent Office
Prior art keywords
drill
hammer
accordance
elastomeric material
hammer 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.)
Not-in-force
Application number
EP05024979A
Other languages
German (de)
English (en)
Other versions
EP1787761A1 (fr
Inventor
Michael Keller
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.)
Metabowerke GmbH and Co
Original Assignee
Metabowerke GmbH and Co
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 Metabowerke GmbH and Co filed Critical Metabowerke GmbH and Co
Priority to EP05024979A priority Critical patent/EP1787761B1/fr
Priority to DE502005008837T priority patent/DE502005008837D1/de
Priority to AT05024979T priority patent/ATE454248T1/de
Priority to US11/594,207 priority patent/US20070107920A1/en
Priority to CN2006101464206A priority patent/CN101181784B/zh
Publication of EP1787761A1 publication Critical patent/EP1787761A1/fr
Application granted granted Critical
Publication of EP1787761B1 publication Critical patent/EP1787761B1/fr
Not-in-force 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
    • B25D17/24—Damping the reaction force
    • 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
    • B25D2222/00—Materials of the tool or the workpiece
    • B25D2222/54—Plastics
    • B25D2222/57—Elastomers, e.g. rubber

Definitions

  • the invention relates to a motor-driven rotary hammer with impact and rotary drive and with a mounted in a housing sleeve according to the preamble of claim 1.
  • a hammer drill is from the EP 1 252 976 A1 known.
  • the present invention has for its object to provide an effective vibration reduction in rotary hammers.
  • the drill sleeve is connected at its outer periphery with a spring means of an elastomeric material having a wall thickness of 1 - 10 mm, and that the spring means holds a Tilgermasse, the in Consequence of the elasticity of the spring means in the circumferential direction and in the longitudinal direction of the drill sleeve relative to this is deflected and can cause a damping to reduce vibration.
  • the absorber mass can oscillate both in a translatory and in a rotational direction.
  • the spring / mass system is designed so that the oscillation of the absorber mass in translational and rotational direction in each case takes place in phase opposition to the vibrations of the drill sleeve, so that these frequencies are eradicated or effectively damped.
  • the overall vibration excitation of the hammer drill is reduced by these two main components.
  • the grip vibrations are generated primarily by the impact and rotational forces exerted on the tool.
  • vibration damping can be used to reduce vibration in an advantageous manner.
  • the inventive construction a very effective vibration reduction can be achieved because both translational and rotational vibrations can be damped.
  • the inventive arrangement of the absorber mass can be eradicated by a single mass at least two dominant exciter frequencies.
  • the interpretation of the Spring / mass system is dependent on the geometry and the amount of the absorber mass and the geometry and design of the spring means of elastomeric material. For example, if the Tilgerfrequenz is to be reduced, it is conceivable to form the elastomeric mass up to 10 mm thick or to increase the amount of absorber mass. This must be designed in each case by suitable design of the spring / mass system according to the frequencies to be canceled, which occur during operation of the hammer drill.
  • the elastomeric material surrounds the drill sleeve in the circumferential direction continuously and is substantially cylindrical. In this case, a very durable connection of the absorber mass to the drill sleeve can be achieved, which is also largely insensitive with regard to shear stress.
  • the elastomeric material has a wall thickness of 4 to 8 mm. Furthermore, an embodiment is preferred in which the elastomeric material has an axial extent in the longitudinal direction of the drill sleeve of 5 to 20 mm.
  • the absorber mass is formed substantially cylindrical. This allows a symmetrical and in the circumferential direction evenly distributed mass distribution around the drill sleeve to be achieved, which proves to be useful in terms of vibration damping.
  • the axial extension of the absorber mass may advantageously also be 5 to 20 mm. It is advantageously 3 to 8 times their wall thickness.
  • the absorber mass / spring system is designed so that vibrations between 30 and 100 Hz are attenuated.
  • the vibrations to be settled are predominantly between 70 and 80 Hz.
  • the figures show an area encompassing the drive components of a hammer drill according to the invention.
  • a region comprising the electric motor and a grip region of the hammer drill are not shown.
  • a main drive shaft extends through the indicated rotary feedthrough 4 in the area 2 and drives (in a manner not shown) to a shaft 6 at.
  • the shaft 6 carries a swash plate assembly 8 (best FIG. 2 it can be seen), the hammer mechanism 10 of the hammer drill drives, and a gear 12 (only off FIG. 2 visible), which causes a rotary drive for a drill sleeve 14.
  • the percussion mechanism 10 comprises a sleeve chamber 18 delimiting a cylinder chamber 16 which can be moved axially back and forth by the swash plate arrangement 8 in the longitudinal direction 20 of the drill sleeve 14.
  • the sleeve 18 is disposed within the drill sleeve 14 and concentrically to this and axially movable relative to this.
  • a free-flying body is provided as a racket 22, which forms an air spring 24 together with the sleeve 18.
  • a spring means 32 of an elastomeric material 34 is provided on the outer circumference 31 of the drill sleeve 14.
  • the spring means 32 and the elastomeric material 34 surrounds the outer periphery 30 of the drill sleeve 15 in the illustrated exemplary case in the circumferential direction continuously; it is substantially cylindrical and has a wall thickness of 1 to 10, in particular from 4 to 8 mm.
  • the elastomeric material 34 carries radially outside and in the illustrated case concentric with the drill sleeve 14 a damping mass 36 also cylindrical basic geometry.
  • the absorber mass 36 is deflectable via the spring means 32 of elastomeric material not only in the axial longitudinal direction 20, but also in the circumferential direction with respect to the drill sleeve 14.
  • the Tilgermasse / spring system is designed so that this absorber mass in translational and rotational direction in each case in phase opposition to the excitation vibrations acting on the drill sleeve can swing through the yielding deflectable arrangement of the absorber mass, so that thereby vibrations dampened or eradicated what is an effective vibration reduction.
  • the total vibration excitation of the hammer drill can thus be reduced by two main components.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Earth Drilling (AREA)
  • Drilling And Boring (AREA)
  • Perforating, Stamping-Out Or Severing By Means Other Than Cutting (AREA)

Claims (10)

  1. Marteau perforateur actionné par un moteur, comportant un système d'entraînement en percussion et rotation et comportant un mandrin porte-foret (14), logé dans un carter et relié en transmission avec un outil ou un porte-outil destiné à recevoir l'outil, caractérisé en ce que le mandrin porte-foret (14), sur son pourtour extérieur (30), est relié à un moyen à ressort (32) réalisé dans un matériau élastomère (34) avec une épaisseur de paroi de 1 à 10 mm, et en ce que le moyen à ressort (32) porte une masse d'amortissement (36) qui, compte tenu de l'élasticité du moyen à ressort (32) dans la direction circonférentielle et dans la direction longitudinale (20) du mandrin porte-foret (14), peut être déviée par rapport à celui-ci et peut induire ainsi un amortissement destiné à réduire les vibrations.
  2. Marteau perforateur selon la revendication 1, caractérisé en ce que le matériau élastomère (34) entoure le mandrin porte-foret (14) en continu dans la direction circonférentielle et est réalisé avec une forme sensiblement cylindrique.
  3. Marteau perforateur selon la revendication 1, caractérisé en ce que le matériau élastomère est segmenté.
  4. Marteau perforateur selon la revendication 1, caractérisé en ce que le matériau élastomère comporte des trous débouchants, des évidements ou ouvertures orientés dans la direction radiale, tangentielle ou axiale.
  5. Marteau perforateur selon l'une quelconque des revendications précédentes, caractérisé en ce que le matériau élastomère (34) a une épaisseur de paroi de 4 à 8 mm.
  6. Marteau perforateur selon l'une quelconque des revendications précédentes, caractérisé en ce que le matériau élastomère (34) a une dimension axiale de 5 à 20 mm dans la direction longitudinale (20) du mandrin porte-foret (14).
  7. Marteau perforateur selon l'une quelconque des revendications précédentes, caractérisé en ce que la masse d'amortissement (36) est réalisée avec une forme sensiblement cylindrique.
  8. Marteau perforateur selon l'une quelconque des revendications précédentes, caractérisé en ce que la masse d'amortissement (36) a une dimension axiale de 5 à 20 mm dans la direction longitudinale (20) du mandrin porte-foret (14).
  9. Marteau perforateur selon l'une quelconque des revendications précédentes, caractérisé en ce que la masse d'amortissement (36) a une dimension axiale dans la direction longitudinale (20) du mandrin porte-foret (14), laquelle est égale à 3 à 8 fois son épaisseur de paroi.
  10. Marteau perforateur selon l'une quelconque des revendications précédentes, caractérisé en ce que la masse amortissante ou système à ressort est configuré de manière à amortir sur de petits marteaux perforateurs des vibrations entre 30 et 100 Hz, et en particulier entre 70 et 80 Hz.
EP05024979A 2005-11-16 2005-11-16 Perçeuse motorisée à percussion Not-in-force EP1787761B1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP05024979A EP1787761B1 (fr) 2005-11-16 2005-11-16 Perçeuse motorisée à percussion
DE502005008837T DE502005008837D1 (de) 2005-11-16 2005-11-16 Motorisch angetriebener Bohrhammer
AT05024979T ATE454248T1 (de) 2005-11-16 2005-11-16 Motorisch angetriebener bohrhammer
US11/594,207 US20070107920A1 (en) 2005-11-16 2006-11-08 Motor driven drilling hammer
CN2006101464206A CN101181784B (zh) 2005-11-16 2006-11-13 电动机驱动的锤钻

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP05024979A EP1787761B1 (fr) 2005-11-16 2005-11-16 Perçeuse motorisée à percussion

Publications (2)

Publication Number Publication Date
EP1787761A1 EP1787761A1 (fr) 2007-05-23
EP1787761B1 true EP1787761B1 (fr) 2010-01-06

Family

ID=36118295

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05024979A Not-in-force EP1787761B1 (fr) 2005-11-16 2005-11-16 Perçeuse motorisée à percussion

Country Status (5)

Country Link
US (1) US20070107920A1 (fr)
EP (1) EP1787761B1 (fr)
CN (1) CN101181784B (fr)
AT (1) ATE454248T1 (fr)
DE (1) DE502005008837D1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010041928A1 (de) * 2010-10-04 2012-04-05 Robert Bosch Gmbh Mehrdimensionaler Schwingungstilger
US9308636B2 (en) 2012-02-03 2016-04-12 Milwaukee Electric Tool Corporation Rotary hammer with vibration dampening
US9849577B2 (en) 2012-02-03 2017-12-26 Milwaukee Electric Tool Corporation Rotary hammer
ES2910664T3 (es) 2015-07-24 2022-05-13 Inventio Ag Dispositivo de montaje automatizado para realizar instalaciones en un hueco de ascensor de un sistema de ascensor
US10814468B2 (en) 2017-10-20 2020-10-27 Milwaukee Electric Tool Corporation Percussion tool
CN214723936U (zh) 2018-01-26 2021-11-16 米沃奇电动工具公司 冲击工具
CN215617869U (zh) 2018-04-04 2022-01-25 米沃奇电动工具公司 一种适于向工具头施加轴向冲击的旋转锤

Family Cites Families (19)

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Publication number Priority date Publication date Assignee Title
DE2851160A1 (de) * 1978-11-25 1980-06-04 Wacker Werke Kg Vorrichtung zum mindern der geraeuschentwicklung an den werkzeugen von bohr- und aufbruchhaemmern
JPS5838230U (ja) * 1981-09-09 1983-03-12 株式会社共立 刈払機の防振装置
US4905772A (en) * 1988-09-01 1990-03-06 Honsa Thomas W Rotary power tool with vibration damping
US5172771A (en) * 1990-11-06 1992-12-22 Charles Machine Works, Inc. Reversible impact-operated boring tool
US5332131A (en) * 1992-09-28 1994-07-26 Pehr Harold T Kicker latch for container closures
DE69329686T2 (de) * 1993-01-27 2001-06-07 Lord Corp Vibrationsdämpfer für handbetätigte vibrierende Vorrichtung
US5839517A (en) * 1993-01-27 1998-11-24 Lord Corporation Vibration isolator for hand-held vibrating devices
JPH09303354A (ja) * 1996-05-21 1997-11-25 Kioritz Corp 抜け止め構造体、及び、該抜け止め構造体を備えた刈払機
US5813477A (en) * 1996-05-23 1998-09-29 Chicago Pneumatic Tool Company Vibration-reduced impact tool and vibration isolator therefor
JPH11104974A (ja) * 1997-10-06 1999-04-20 Makita Corp 打撃工具
DE19933972A1 (de) * 1999-07-20 2001-01-25 Bosch Gmbh Robert Bohr- oder Schlaghammer
DE10021355B4 (de) * 2000-05-02 2005-04-28 Hilti Ag Schlagendes Elektrohandwerkzeuggerät mit schwingungsentkoppelten Baugruppen
ES2208623T3 (es) * 2001-03-07 2004-06-16 Black & Decker Inc. Martillo.
GB0109747D0 (en) * 2001-04-20 2001-06-13 Black & Decker Inc Hammer
DE10294312T5 (de) * 2001-09-17 2004-09-02 Milwaukee Electric Tool Corp., Brookfield Rotationshammer
JP4195818B2 (ja) * 2003-01-16 2008-12-17 株式会社マキタ 電動ハンマ
GB2413611B (en) * 2003-03-21 2006-01-25 Black & Decker Inc Impact system for heavy-duty hammer and rock drills
EP1464449B1 (fr) * 2003-04-01 2010-03-24 Makita Corporation Outil électrique
DE602004026243D1 (de) * 2003-05-09 2010-05-12 Makita Corp Elektrowerkzeug

Also Published As

Publication number Publication date
US20070107920A1 (en) 2007-05-17
CN101181784A (zh) 2008-05-21
ATE454248T1 (de) 2010-01-15
EP1787761A1 (fr) 2007-05-23
CN101181784B (zh) 2010-05-12
DE502005008837D1 (de) 2010-02-25

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