EP2480381B1 - Entraînement à bielle avec élément oscillant supplémentaire - Google Patents

Entraînement à bielle avec élément oscillant supplémentaire Download PDF

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Publication number
EP2480381B1
EP2480381B1 EP10739559.2A EP10739559A EP2480381B1 EP 2480381 B1 EP2480381 B1 EP 2480381B1 EP 10739559 A EP10739559 A EP 10739559A EP 2480381 B1 EP2480381 B1 EP 2480381B1
Authority
EP
European Patent Office
Prior art keywords
drive
movement
electric tool
eccentric
oscillator
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
EP10739559.2A
Other languages
German (de)
English (en)
Other versions
EP2480381A1 (fr
Inventor
Carsten Diem
Willy Braun
Hardy Schmid
Holger Ruebsaamen
Jan Koalick
Peter Loehnert
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2480381A1 publication Critical patent/EP2480381A1/fr
Application granted granted Critical
Publication of EP2480381B1 publication Critical patent/EP2480381B1/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
    • 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
    • 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
    • B25D2217/0088—Arrangements for damping of the reaction force by use of counterweights being mechanically-driven

Definitions

  • the present invention relates to a tool according to the preamble of claim 1.
  • a tool is known from EP 1 475 190 A2 known.
  • a typical housing vibration of drills and percussion hammers which have a striking mechanism assembly in which a piston is driven by an eccentric, is composed of several frequency components.
  • causes of the housing vibrations are, for example, air forces the pneumatic percussion, mass forces of the connecting rod piston drive and repercussions of the insert tool.
  • a balancing mass is coupled to the drive of the electric tool and is driven in such a way that the reaction force resulting from the drive of the counteroscillator works as well as possible against the vibration source.
  • balancing mass of a counter-oscillator can be divided into two classes: In the first case, the balancing mass is forcibly driven by means of an eccentric crank or cross-grinding drive.
  • the balancing mass is driven by cams, wherein the required contact contact is made by means of a spring loading of the balancing mass. In this case, the balancing mass is not forced.
  • Examples of a force-driven balancing mass show the publications EP 1 475 190 A2 and EP 1 439 038 A1 .
  • the balancing mass is arranged around the hammer tube and is driven by an additional connecting rod linked to the striking mechanism eccentric.
  • the EP 1 439 038 A1 is a cuboid, provided with a transverse slot balancing mass disposed above the eccentric. In the transverse slot runs to the axis of rotation eccentric bolt of Schlagtechniksexzenters so that the balancing mass is driven by a cross-loop.
  • the hitherto known embodiments have in common that they primarily attenuate caused by the percussion mechanism housing vibration. Frequency components from other sources of vibration, for example by a center of gravity, which leads to not acting in the direction of impact housing vibrations, can not be adequately compensated with the previously known embodiments.
  • the object of the invention is therefore to provide a power tool with a counteroscillator, with which the housing oscillation of the power tool is better compensated, and in particular with the vibration caused by a percussion mechanism also vibrations from other sources of vibration can be compensated.
  • a power tool with impact mechanism assembly according to claim 1, which is driven cyclically in and against a direction of impact, and with a Gezogenschwinger to compensate for vibrations of the power tool, in particular of housing vibrations, comprising a balancing mass, wherein the balancing mass can be driven by driving the percussion mechanism in a direction of movement, wherein the direction of movement extends at an angle to the direction of impact.
  • the counteroscillator in this case comprises a drive means for driving the compensating mass that is provided eccentrically rotatable about an eccentric axis.
  • a drive means is easily and inexpensively providable on the eccentric disc.
  • the drive means is an eccentric pin, on which a connecting rod for driving the percussion mechanism assembly is arranged. Therefore, a component already required for driving the striking mechanism assembly is also used for driving the counter-oscillator.
  • a vibration-generating vibration can be counteracted by generating a counter-vibration of the same amount in the opposite direction.
  • the direction of movement extends at an angle to the direction of impact.
  • the direction of movement of the balancing mass is better adapted to the direction of vibration-generating vibrations in the power tool. Because in the power tool not only vibration-generating vibrations in the direction of impact are effective, but other sources of vibration cause vibrations that act at an angle to the direction of impact. Such vibrations arise, for example, from the center of gravity of the power tool.
  • the angle, in which the balance mass moves substantially corresponds to the direction of movement, against which the sum of the vibration-generating vibrations acts, these can be at least partially compensated.
  • the power tool has an eccentric disc, which is rotatable in a rotational direction concentrically about the eccentric axis, wherein the direction of movement of the balancing mass has a first movement component which extends in the direction of the eccentric axis.
  • a direction of movement is formed from a sum of movement components which extend parallel to the coordinates of a Cartesian coordinate system. Therefore, this embodiment makes it possible to compensate for vibration-generating vibrations that extend in the direction of the eccentric axis.
  • the movement direction further comprises a second movement component in the direction of impact, and / or a third component of movement transverse to the direction of impact and transversely to the direction of the eccentric axis. Therefore, vibration-generating vibrations acting in at least two or all three spatial directions can be compensated.
  • the direction of movement changes when driving the percussion unit.
  • the center of gravity of the power tool also called momentary pole, changes during its use. This changes the vibration-generating vibration, in particular its direction.
  • By adjusting the direction of movement such changing vibration-generating vibrations can be at least partially compensated.
  • the counteroscillator preferably comprises a drive means for driving the balancing mass that is provided eccentrically rotatable about the eccentric axis.
  • a drive means for driving the balancing mass that is provided eccentrically rotatable about the eccentric axis.
  • Such a drive means is easily and inexpensively providable on the eccentric disc.
  • the drive means is an eccentric pin on which a connecting rod for driving the percussion mechanism assembly is arranged. Therefore, a component already required for driving the striking mechanism assembly is also used for driving the counter-oscillator.
  • the balancing mass can be moved back and forth substantially in the direction of movement from a starting point and returns to the starting point.
  • the balancing mass is therefore cyclically reciprocated by the drive means.
  • the balancing mass is preferably forcibly driven.
  • a transmission of motion between the drive means and the leveling compound is clear even at high reaction forces and high operating frequency.
  • no additional pressure means such as springs are needed, so that the effort, space and cost is reduced compared to non-positively driven embodiments of counter-oscillators.
  • no energy required for the pressing force or due to friction and additional wear effects, must be provided by the engine power.
  • the direction of movement changes when driving the percussion unit.
  • the center of gravity of the power tool also called momentary pole, changes during its use. This changes the vibration-generating vibration, in particular its direction.
  • By adjusting the direction of movement such changing vibration-generating vibrations can be at least partially compensated.
  • the balancing mass can be moved back and forth substantially in the direction of movement from a starting point and returns to the starting point.
  • the balancing mass is therefore cyclically reciprocated by the drive means.
  • the balancing mass is preferably forcibly driven.
  • a transmission of motion between the drive means and the leveling compound is clear even at high reaction forces and high operating frequency.
  • no additional pressure means such as springs are needed, so that the cost, space and cost is reduced compared to non-positively driven embodiments of counter-oscillators.
  • no energy required for the pressing force or due to friction and additional wear effects, must be provided by the engine power.
  • the counteroscillator comprises a drive pulley, which cooperates with the drive means, wherein by driving the percussion mechanism assembly, the drive pulley is rotatable about a drive axis.
  • the drive axle preferably extends parallel to the eccentric axis.
  • the drive axle extends at a second angle to the eccentric axis. In this case, the second angle is the same angle or an angle other than the angle of the direction of movement to the direction of impact.
  • the counteroscillator is arranged in a cover assembly of the power tool.
  • the power tool can be retrofitted with a counteroscillator according to the invention.
  • an exchange of Schwarzschwingers, for example, to adapt the power tool to different operating modes is possible.
  • An inventive power tool is, for example, a percussion hammer or a hammer drill.
  • Fig. 1 shows an embodiment of a power tool 1 according to the invention.
  • the power tool 1 is a hammer drill.
  • the electric tool 1 is driven by means of an electric motor 20, wherein the electric motor 20 drives a motor shaft 21 with a drive pinion 22, and wherein the drive pinion 22 drives a drive wheel 23 which is arranged concentrically in a rotational direction 8 about an eccentric axis 9. Furthermore, an eccentric disk 10 is arranged concentrically rotatable about the eccentric axis 9, so that by driving the drive wheel 23, the eccentric disk 10 is driven.
  • a connecting rod 12 is eccentrically arranged eccentrically about the eccentric axis 33 by means of an eccentric pin 11.
  • the rotational movement of the eccentric disk 10 is converted into a translational movement to a Piston 121 a percussion unit 3, which is arranged on the connecting rod 12, cyclically in or against a direction of impact 4 to drive.
  • the power tool 1 has a counteroscillator 5, which is arranged in a cover assembly 19 of the power tool 1.
  • the counteroscillator 5 is driven by means of a drive means 11, which is formed here by the eccentric pin 11.
  • the eccentric pin 11 engages in a recess 161 of a drive pulley 16 of the counter-oscillator 5.
  • the drive pulley 16 is arranged substantially parallel to the eccentric disk 10, and mounted rotatably about a drive axle 17. In the embodiment shown here, the drive axle 17 extends substantially parallel to the eccentric axis 9.
  • the counteroscillator 5 has a balancing mass 2, which is displaceable along a guide means 24, which is arranged in the cover assembly 19, in a direction of movement 6.
  • the leveling compound 2 is arranged on a push rod 18 and in particular rotatable in the slot 24 in the cylindrically.
  • the push rod 18 is further arranged eccentrically on the drive pulley 16, in particular by means of a ball joint. When driving the drive pulley 16, the rotational movement of the drive pulley 16 is therefore converted into a translatory thrust movement of the balancing mass 2 in the direction of movement 6.
  • the direction of movement 6 extends at an angle 7 to the direction of impact 4. It is in a Cartesian coordinate system x, y, z in a first movement component 61, here in the y direction of the coordinate system, which runs parallel to the eccentric axis 9, and a second movement component 62, here in the z direction of the coordinate system, which runs parallel to the direction of impact 4, can be dismantled. Since the direction of movement 6 of the balancing mass 2 is formed not only from a movement component 62 extending parallel to the direction of impact 4, but also from a movement component 61 extending transversely to the direction of impact 4, vibration-generating oscillations which are not in the direction of impact can also be compensated with this counteroscillator 5 4 act.
  • Power tools 1 with counter-oscillators 5 are also possible, in which the direction of movement 6 of the balancing mass 2 has a third movement component (not shown here) which extends in the third spatial direction, in this case the x direction of a Cartesian coordinate system.
  • Fig. 2 shows a further embodiment of a power tool according to the invention 1.
  • the embodiment has another counteroscillator 5, which is also disposed in the lid assembly 19.
  • the counter-oscillator 5 of this embodiment also has, as a drive means 11, the eccentric pin 11 with which the connecting rod 12 is arranged to drive the piston 121 in the direction of impact 4 on the eccentric disk 10. Therefore, the terms eccentric pin 11 and drive means 11 are also used synonymously here.
  • a gate 13 is provided, in which the eccentric pin 11 engages, and which is rigidly connected to a slide bar 131, which is arranged slidably in the cover assembly 19 substantially in the direction of impact 4.
  • the balancing mass 2 is arranged on a pivoting oscillator 14, which is mounted rotatably about a pivot axis 15 in the cover assembly 19.
  • the pivoting oscillator 14 has a mouth opening 141 into which a bolt 132 engages, which is arranged on the link 13.
  • the bolt 132 is arranged on the slide bar 131.
  • the pivoting oscillator 14 When moving the slide bar 131 in the direction of impact 4, the pivoting oscillator 14 is pivoted about the pivot axis 15. As a result, the balancing mass 2 is pivoted concentrically about the pivot axis 15. If the slide bar 131 is pushed back against the direction of impact 4, the pivoting oscillator 14 is pivoted back about the pivot axis 15, so that the balancing mass 2 is also pivoted back.
  • the leveling compound 2 is therefore cyclically swung back and forth in this embodiment.
  • the direction of movement 6 of the balancing mass 2 changes when driving the counter-oscillator 5. Because the balancing mass pivots along a circular path 60 concentrically about the pivot axis 15 back and forth. For each moment, the direction of movement 6 can be found by applying a tangent to the circular path 60. As Fig. 2 shows, here the movement direction 6 is composed of a first movement component 61 parallel to the eccentric axis 9 and a second movement component 62 parallel to the direction of impact 4 together.
  • the movement direction 6 also has a third movement component (not shown here) in the third spatial direction, here the x direction of the Cartesian coordinate system.
  • vibration-generating vibrations are compensated, change the effective direction during operation of the power tool 1.
  • Fig. 3 shows a section of a further embodiment of a power tool 1 according to the invention with a counteroscillator 5.
  • Analogous to the embodiment of Fig. 2 is the balancing mass 2 of this counter-oscillator 5 is arranged on a pivoting rocker 14 which is rotatably mounted about a pivot axis 15.
  • the pivoting oscillator 14 likewise has the mouth opening 141 into which the bolt 132 engages, which is arranged on the link 13, which is rigidly connected to the slide rod 131, which is drivable by means of the eccentric pin 11.
  • this pivoting oscillator 14 has a second mouth opening 142, in which a second pin 241, which is arranged on the mass 2, engages.
  • the mass 2 is in a gate 24, for example, a housing of the power tool 1 (s. Fig. 1 . 2 ) stored.
  • the gate 24 extends substantially in a gate direction 242.
  • the movement direction 6 is in turn composed of a first movement component 61 parallel to the eccentric axis 9 and a second movement component 62 parallel to the direction of impact 4, so that also with this embodiment analogous to the embodiment of Fig. 1 With this counter-oscillator 5 vibration-generating vibrations can be compensated, which do not act in the direction of impact 4.
  • the movement direction 6 has a third movement component (not shown here) in the third spatial direction, here the x direction of the Cartesian coordinate system.
  • the balancing mass 2 moving at an angle 7 to the direction of impact 4, apart from the compensation of vibrations caused by the striking mechanism assembly 3, also enables the compensation of further vibration-generating vibrations caused by vibration sources which are not in the direction of impact 4 act.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)

Claims (10)

  1. Outil électrique (1) doté d'un module de frappe (3) entraîné de façon cyclique dans une direction de frappe (4) et dans la direction opposée et avec un contre-élément oscillant (5) servant à compenser les vibrations de l'outil électrique (1), notamment les oscillations de carter, le contre-élément oscillant (5) comprenant une masse d'équilibrage (2) et un moyen d'entraînement (11) servant à entraîner la masse d'équilibrage (2) et étant placé de façon excentrée de façon à pouvoir pivoter autour d'un axe excentré (9),
    la masse d'équilibrage (2) étant entraînée dans une direction de déplacement (6) par l'intermédiaire d'un entraînement du module de frappe (3) ;
    le moyen d'entraînement (11) étant une broche excentrée au niveau de laquelle une bielle (12) est disposée pour entraîner le module de frappe (3) ;
    caractérisé en ce que :
    la direction de déplacement (6) s'étend selon un angle (7) par rapport à la direction de frappe (4).
  2. Outil électrique (1) selon la revendication 1, caractérisé en ce qu'il comporte un disque excentré (10) pouvant être pivoté dans une direction de rotation (8) concentriquement autour de l'axe excentré (9), la direction de déplacement (6) de la masse d'équilibrage (2) comportant une première composante de mouvement (61) s'étendant en direction de l'axe excentré (9).
  3. Outil électrique (1) selon la revendication 2, caractérisé en ce que la direction de déplacement (6) comporte une deuxième composante de mouvement (62) dans la direction de frappe (4), et/ou une troisième composante de mouvement (63) s'étendant transversalement à la direction de frappe (4) ainsi que transversalement à la direction de l'axe excentré (9).
  4. Outil électrique (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que la direction de déplacement (6) varie lorsque le module de frappe (3) est entraîné.
  5. Outil électrique (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que la masse d'équilibrage (2) est entraînée de façon contrainte.
  6. Outil électrique (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que le contre-élément oscillant (5) comprend une coulisse (13) dans laquelle le moyen d'entraînement (11) s'engrène, la coulisse (13) pouvant se déplacer selon un mouvement de va-et-vient de translation par le biais de l'entraînement du module de frappe (3).
  7. Outil électrique (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que la masse d'équilibrage (2) est disposée au niveau d'un élément oscillant (14) basculant disposé de façon à pouvoir tourner autour d'un axe de basculement (15) et interagissant avec la coulisse (13), de sorte que la masse d'équilibrage (2) peut basculer autour de l'axe de basculement (15) par entraînement de la coulisse (13).
  8. Outil électrique (1) selon l'une quelconque des revendications 1 à 5, caractérise en ce que le contre-élément oscillant (5) comprend un disque d'entraînement (16) interagissant avec le moyen d'entraînement (11), le disque d'entraînement (16) pouvant pivoter autour d'un axe d'entraînement (17) par entraînement du module de frappe (3).
  9. Outil électrique (1) selon la revendication 8, caractérisé en ce que la masse d'équilibrage (2) est disposée au niveau d'une barre de poussée (18) disposée de façon excentrée au niveau du disque d'entraînement (16) et interagissant avec la masse d'équilibrage (2), de sorte que la masse d'équilibrage (2) peut être déplacée en translation par entraînement du disque d'entraînement (16) autour de l'axe d'entraînement (17).
  10. Outil électrique (1) selon l'une quelconque des revendications précédentes, caractérisé en ce que le contre-élément oscillant (5) est disposé dans un module de couvercle (19) de l'outil électrique (1).
EP10739559.2A 2009-09-24 2010-07-27 Entraînement à bielle avec élément oscillant supplémentaire Not-in-force EP2480381B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009044934A DE102009044934A1 (de) 2009-09-24 2009-09-24 Pleuelantrieb mit Zusatzschwinger
PCT/EP2010/060848 WO2011035954A1 (fr) 2009-09-24 2010-07-27 Mécanisme d'entraînement de bielle doté d'un balancier supplémentaire

Publications (2)

Publication Number Publication Date
EP2480381A1 EP2480381A1 (fr) 2012-08-01
EP2480381B1 true EP2480381B1 (fr) 2013-05-15

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP10739559.2A Not-in-force EP2480381B1 (fr) 2009-09-24 2010-07-27 Entraînement à bielle avec élément oscillant supplémentaire

Country Status (5)

Country Link
US (1) US20120227995A1 (fr)
EP (1) EP2480381B1 (fr)
CN (1) CN102510792B (fr)
DE (1) DE102009044934A1 (fr)
WO (1) WO2011035954A1 (fr)

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DE102012206445A1 (de) * 2012-04-19 2013-10-24 Hilti Aktiengesellschaft Werkzeugmaschine
DE102012209868A1 (de) * 2012-06-13 2013-12-19 Robert Bosch Gmbh Getriebegehäuse
US10632605B2 (en) * 2014-04-30 2020-04-28 Koki Holdings Co., Ltd. Work tool
CN105465271B (zh) * 2014-06-23 2019-02-22 博世电动工具（中国）有限公司 平衡重机构和电动工具
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
CN115648129B (zh) * 2022-10-29 2024-06-21 江苏东成工具科技有限公司 冲击电动工具

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US3028841A (en) * 1958-06-18 1962-04-10 Leavell Charles Vibration elimination
EP1415768A1 (fr) * 2002-10-31 2004-05-06 Atlas Copco Electric Tools GmbH Amortisseur d'oscillations
JP4195818B2 (ja) 2003-01-16 2008-12-17 株式会社マキタ 電動ハンマ
EP1710052B1 (fr) 2003-03-21 2014-11-19 Black & Decker, Inc. Outil de percussion électrique avec moyens de limitation des vibrations
DE602004026243D1 (de) 2003-05-09 2010-05-12 Makita Corp Elektrowerkzeug
DE102004012820B3 (de) * 2004-03-16 2005-11-17 Wacker Construction Equipment Ag Taumelfingergetriebe
CN101412213A (zh) * 2007-10-19 2009-04-22 喜利得股份公司 具有振荡平衡质量的手工工具机
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
DE102007061716A1 (de) * 2007-12-19 2009-06-25 Robert Bosch Gmbh Taumelantrieb einer Handwerkzeugmaschine
DE102008000625A1 (de) * 2008-03-12 2009-09-17 Robert Bosch Gmbh Handwerkzeugmaschine
DE102008044219A1 (de) * 2008-12-01 2010-06-02 Robert Bosch Gmbh Handwerkzeugmaschinenvorrichtung
US7938196B2 (en) * 2009-04-17 2011-05-10 Hilti Aktiengesellschaft Hand-held power tool with vibration-compensating mass

Also Published As

Publication number Publication date
US20120227995A1 (en) 2012-09-13
WO2011035954A1 (fr) 2011-03-31
DE102009044934A1 (de) 2011-03-31
CN102510792B (zh) 2014-11-12
EP2480381A1 (fr) 2012-08-01
CN102510792A (zh) 2012-06-20

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