EP2047952B1 - Machine-outil à main avec masse d'équilibrage de vibration - Google Patents
Machine-outil à main avec masse d'équilibrage de vibration Download PDFInfo
- Publication number
- EP2047952B1 EP2047952B1 EP08105444A EP08105444A EP2047952B1 EP 2047952 B1 EP2047952 B1 EP 2047952B1 EP 08105444 A EP08105444 A EP 08105444A EP 08105444 A EP08105444 A EP 08105444A EP 2047952 B1 EP2047952 B1 EP 2047952B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- balancing mass
- mass
- spring
- power tool
- vibration
- 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
Links
- 150000001875 compounds Chemical class 0.000 description 6
- 238000003466 welding Methods 0.000 description 4
- 239000002184 metal Substances 0.000 description 2
- 230000010355 oscillation Effects 0.000 description 2
- 230000003534 oscillatory effect Effects 0.000 description 2
- 238000009527 percussion Methods 0.000 description 2
- 238000010009 beating Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000005284 excitation Effects 0.000 description 1
- 230000003116 impacting effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000000737 periodic effect Effects 0.000 description 1
Images
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
Definitions
- the invention refers to a hand tool with a striking mechanism, in particular a hammer drill, combination hammer or chisel hammer, with a vibration compensation mass, according to the preamble of claim 1 and as from EP 1415 768 A known.
- a vibration balancing mass is a vibratory subsystem, which consists of an abstract vibratable mass, an abstract spring and an abstract damper, which must not be explicitly designed as a concrete component.
- the abstract damper is often not realized as a concrete component and is still effective by practically always occurring friction and flow losses.
- ordinary passive equalization masses which are exclusively self-excited, of actively controlled equalization compounds, which are deliberately externally excited by a mostly periodic excitation function.
- the axially oscillating, passive vibration compensation mass is hollow-cylindrical; after EP1252976 arranged around the guide tube of the percussion and guided linearly along it.
- the natural frequency of the vibration compensation mass corresponds as exactly as possible to the vibration frequency to be damped.
- the natural frequency depends essentially on the mass of the balancing mass and the spring stiffness.
- the object of the invention consists in the simple realization of respect to the natural frequency closely tolerated vibration compensation masses of hand tool machines in large quantities. Another aspect consists in the technologically simple production of different mass-based balancing weights for vibration compensation masses for various model platforms of hand tool machines.
- a hand tool on an internal (eg gear cover housing) or external (eg outer housing) housing at least one vibration compensating mass with at least one axially oscillatable along a vibration axis, in itself rigid balancing mass, which is axially pressure-biased via at least one spring to the housing, wherein the inherently rigid leveling compound is formed in several parts.
- the partial mass on an adjustment bore which can be done on the diameter of a technologically simple adjustment (via a mandrel used in the tool of different diameters) of the mass of the partial mass by this is reduced by the mass of the Justagezylinders.
- the balancing mass composed of along the swing axis packetized masses, further advantageous with laser welding, plasma welding, sigma welding) welded together, which on the nature and number of packetized masses the mass of the balancing mass for vibration compensation masses for various model platforms of portable power tools is discreetly adjustable.
- the balancing mass is advantageously composed of identical partial masses packed along the oscillating axis, as a result of which the masses are produced in bulk in very large quantities and are advantageously punched out of sheet metal and laser-welded. As a result, tight-tolerance leveling compounds can be produced in large quantities.
- the formed / embossed stop surfaces can be made for the spring ends in a partial mass with high accuracy.
- the spring is arranged with respect to its axial spring length completely within the balancing mass, whereby the total length of the vibration balancing mass is essentially determined by the balancing mass length. Since this is thus the greatest possible, the smallest possible resonance frequencies can be achieved with a fixed oscillation compensation ground length and spring constants.
- the spring is arranged in a pocket-shaped, prismatic recess of the balancing mass, whereby it is at least partially positively guided in the recess and thus can not break across at pressure threshold stress.
- the spring is arranged on both sides of the end face around a respective stop mandrel, which is further advantageous sleeve-shaped, whereby the spring via a mutually approaching displacement of the fixed to the housing stop pins is druckvorspannbar and thus allow axial limited oscillation of the balancing mass.
- FIG. 1 has a with respect to a striking axis A axially beating and rotating hand tool 1 on a along the striking axis A vibrating housing 2 (shown on the outer housing, but analogous to a dashed shown to vibration isolated inner housing of a percussion 17) fixed vibration compensation mass 3 with a vibratory leveling compound 4, which is mounted axially resiliently via a spring 5 to the outer housing 2.
- the mirror plane S with the axis of impact A mirror-symmetrical vibration compensation mass 3 is fixed by means of fixing means 6 in the form of screws on the housing 2 of the power tool 1 on the handle 7 opposite convex upper housing 8.
- the matching concave trained, inherently rigid balancing mass 4 is disposed within a majority of these in the plane of representation transverse to the impact axis A (except for the housing top 8 facing sector) comprehensive Schwingungsaus GmbHsmassengephaseuse 9 and axially movable on this along the striking axis A extending guide surfaces 10 guided.
- the exactly one spring 5 is arranged in a prismatic, pocket-shaped in the representation plane transverse to the impact axis A, recess 11 of the leveling compound 4.
- Fig. 2a, 2b is in a variant of the vibration-compensating mass 3 ', the inherently rigid balancing mass 4' in several parts of many welded together, along the swing axis A packetized and (except for the two end-side) identical part masses 12th composed.
- the two springs 5 with respect to their axial spring length completely within the plane mirrored to the mirror plane S with the striking axis A mirror-symmetrical compensating mass 4 'and on both sides at the front by one on the housing 2 (FIG. Fig. 1 ) arranged stop mandrel 16 around, which is itself formed sleeve-shaped.
- the axially compressed stop pins 16 on the housing 2 ( Fig. 1 ) whereby the compensating mass 4 'with respect to the stop pins 16 and the housing 2 ( Fig. 1 ) is axially oscillatable.
- FIG. 3 and FIG. 4 is formed mirror-symmetrical to the mirror plane S with the striking axis
- a two-fold rotationally symmetrical Fig. 3 is the balancing mass 4 'composed of two diametrically oriented, identical partial masses 12' and spot welded together at welding points 13.
- the two diametrically oriented, identical sub-masses 12 are formed shell-shaped as sheet-metal bent parts and riveted to one another with rivets 14.
- the subassembly 12" has an adjustment bore 15.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Percussive Tools And Related Accessories (AREA)
- Vibration Prevention Devices (AREA)
Claims (7)
- Machine-outil à main comportant au moins une masse de compensation de vibrations (3, 3') fixée sur un boîtier (2), ayant au moins une masse de compensation rigide en elle-même (4, 4', 4''), pouvant vibrer axialement le long d'un axe de vibration (A), laquelle masse de compensation est montée de manière à faire axialement ressort par l'intermédiaire d'au moins un ressort (5) par rapport au boîtier (2), dans laquelle la masse de compensation rigide en elle-même (4, 4', 4") est formée à partir de masses partielles (12, 12', 12") rigidement reliées, caractérisée en ce que le ressort (5) est agencé entièrement à l'intérieur de la masse de compensation (4, 4', 4") par rapport à sa longueur de ressort axiale.
- Machine-outil à main selon la revendication 1, caractérisée en ce que la masse partielle (12") comporte un alésage de réglage (15).
- Machine-outil à main selon la revendication 1, caractérisée en ce que la masse de compensation (4') est assemblée à partir de masses partielles (12) empilées le long de l'axe de vibration (A).
- Machine-outil à main selon la revendication 3, caractérisée en ce que la masse de compensation (4') est assemblée à partir de masses partielles (12) identiques empilées le long de l'axe de vibration (A).
- Machine-outil à main selon la revendication 1, caractérisée en ce que le ressort (5) est agencé dans un évidement prismatique, en forme de poche (11) de la masse de compensation (4, 4', 4").
- Machine-outil à main selon l'une quelconque des revendications 1 à 5, caractérisée en ce que le ressort (5), au niveau de ses deux extrémités, est agencé frontalement autour d'un mandrin de butée (16) respectif.
- Machine-outil à main selon la revendication 1, caractérisée en ce que la masse de compensation est assemblée à partir de deux demies coques identiques (12') qui sont agencées l'une contre l'autre des deux côtés de l'axe de vibration (A).
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102007000837A DE102007000837A1 (de) | 2007-10-09 | 2007-10-09 | Handwerkzeugmaschine mit Schwingungsausgleichsmasse |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2047952A1 EP2047952A1 (fr) | 2009-04-15 |
EP2047952B1 true EP2047952B1 (fr) | 2012-08-22 |
Family
ID=40001439
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08105444A Active EP2047952B1 (fr) | 2007-10-09 | 2008-09-26 | Machine-outil à main avec masse d'équilibrage de vibration |
Country Status (4)
Country | Link |
---|---|
US (1) | US20090090528A1 (fr) |
EP (1) | EP2047952B1 (fr) |
CN (1) | CN101407051B (fr) |
DE (1) | DE102007000837A1 (fr) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9555554B2 (en) | 2013-05-06 | 2017-01-31 | Milwaukee Electric Tool Corporation | Oscillating multi-tool system |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4647957B2 (ja) | 2004-08-27 | 2011-03-09 | 株式会社マキタ | 作業工具 |
US8056747B2 (en) * | 2007-10-12 | 2011-11-15 | General Electric Company | Removable tank for laundry bulk dispenser system |
DE102009054708A1 (de) * | 2009-12-16 | 2011-06-22 | Robert Bosch GmbH, 70469 | Handwerkzeugmaschinenvorrichtung |
DE102009054728A1 (de) * | 2009-12-16 | 2011-06-22 | Robert Bosch GmbH, 70469 | Handwerkzeugmaschine |
DE102009054723A1 (de) * | 2009-12-16 | 2011-06-22 | Robert Bosch GmbH, 70469 | Handwerkzeugmaschine |
DE102010002262A1 (de) * | 2010-02-23 | 2011-08-25 | Robert Bosch GmbH, 70469 | Externer Tilger |
DE102010041938A1 (de) * | 2010-10-04 | 2012-04-05 | Robert Bosch Gmbh | Materialverteilungseinheit |
US10232500B2 (en) * | 2012-12-17 | 2019-03-19 | Swerea Ivf Ab | Impact machine |
CN106715949B (zh) * | 2014-06-16 | 2019-03-08 | 斯威尔Ivf股份有限公司 | 冲击机 |
US11571796B2 (en) * | 2018-04-04 | 2023-02-07 | Milwaukee Electric Tool Corporation | Rotary hammer |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2127821A1 (fr) * | 2008-05-27 | 2009-12-02 | AEG Electric Tools GmbH | Outil électrique doté d'un réducteur de vibrations |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1845825A (en) * | 1927-07-22 | 1932-02-16 | Chicago Pneumatic Tool Co | Spring handle attachment for rock drills |
US1868626A (en) * | 1928-02-04 | 1932-07-26 | Chicago Pneumatic Tool Co | Shock absorbing handle |
DE815179C (de) | 1949-11-17 | 1951-10-01 | Franz Dr-Ing Bollenrath | Drucklufthammer mit Massenausgleich |
US3230831A (en) * | 1963-06-07 | 1966-01-25 | Giddings & Lewis | Vibration damper for machine tools |
DE1281970B (de) | 1964-06-25 | 1968-10-31 | Reichsbahn Vertreten Durch Den | Schwingungstilger fuer Schlaghaemmer |
US3522864A (en) * | 1968-05-08 | 1970-08-04 | Cincinnati Milling Machine Co | Tuned vibration damper assembly for machine tools |
FR2237734A1 (en) | 1973-07-16 | 1975-02-14 | Inst Nal Rech Securite | Oscillating mass shock absorbers for pneumatic drill - two sliding masses sprung above and below flank drill casing |
DE3122979A1 (de) * | 1981-06-10 | 1983-01-05 | Hilti AG, 9494 Schaan | Bohr- oder meisselhammer |
US4612429A (en) * | 1984-08-13 | 1986-09-16 | Westinghouse Electric Corp. | Multiple-impact shock absorbing means for circuit interrupter and other apparatus |
US5471969A (en) * | 1993-09-28 | 1995-12-05 | Mcdonald, Jr.; Norman J. | Stabilizers adapted to be connected to a bow |
GB0109747D0 (en) | 2001-04-20 | 2001-06-13 | Black & Decker Inc | Hammer |
US6719503B1 (en) * | 2001-09-07 | 2004-04-13 | Unova Ip Corp | Tuned damped absorber support |
EP1415768A1 (fr) | 2002-10-31 | 2004-05-06 | Atlas Copco Electric Tools GmbH | Amortisseur d'oscillations |
DE602004026134D1 (de) * | 2003-04-01 | 2010-05-06 | Makita Corp | Kraftwerkzeug |
DE10332637A1 (de) * | 2003-07-18 | 2005-02-03 | Andreas Stihl Ag & Co. Kg | Antivibrationselement |
EP1779979B1 (fr) * | 2004-04-30 | 2018-02-21 | Makita Corporation | Outil de travail |
GB2414702A (en) * | 2004-06-04 | 2005-12-07 | Black & Decker Inc | Vibration Reduction Apparatus for Power Tool |
-
2007
- 2007-10-09 DE DE102007000837A patent/DE102007000837A1/de not_active Withdrawn
-
2008
- 2008-09-23 US US12/284,650 patent/US20090090528A1/en not_active Abandoned
- 2008-09-26 EP EP08105444A patent/EP2047952B1/fr active Active
- 2008-10-07 CN CN2008101689618A patent/CN101407051B/zh active Active
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2127821A1 (fr) * | 2008-05-27 | 2009-12-02 | AEG Electric Tools GmbH | Outil électrique doté d'un réducteur de vibrations |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9555554B2 (en) | 2013-05-06 | 2017-01-31 | Milwaukee Electric Tool Corporation | Oscillating multi-tool system |
Also Published As
Publication number | Publication date |
---|---|
US20090090528A1 (en) | 2009-04-09 |
CN101407051B (zh) | 2012-12-05 |
DE102007000837A1 (de) | 2009-04-16 |
CN101407051A (zh) | 2009-04-15 |
EP2047952A1 (fr) | 2009-04-15 |
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