EP1952952A2 - Oscillation mass damper for hand tools - Google Patents
Oscillation mass damper for hand tools Download PDFInfo
- Publication number
- EP1952952A2 EP1952952A2 EP08100762A EP08100762A EP1952952A2 EP 1952952 A2 EP1952952 A2 EP 1952952A2 EP 08100762 A EP08100762 A EP 08100762A EP 08100762 A EP08100762 A EP 08100762A EP 1952952 A2 EP1952952 A2 EP 1952952A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- spring
- housing
- vibration damper
- damper according
- mass
- 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
Links
- 230000010355 oscillation Effects 0.000 title description 2
- 239000006096 absorbing agent Substances 0.000 claims description 39
- 238000013016 damping Methods 0.000 abstract description 4
- 230000004323 axial length Effects 0.000 abstract 1
- 238000009527 percussion Methods 0.000 abstract 1
- 238000010009 beating Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000011109 contamination Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000003534 oscillatory effect Effects 0.000 description 1
- 230000001360 synchronised 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
-
- 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
- B25D2250/245—Spatial arrangement of components of the tool relative to each other
Definitions
- the invention refers to a vibration damper for a hand tool, in particular a hammer drill, combi hammer or chisel hammer.
- a vibration damper 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 vibration absorbers which are exclusively self-excited, of actively controlled vibration absorbers.
- the hollow cylindrical vibration damper is arranged around the guide tube of the hammer mechanism.
- the compact designed vibration damper is disposed within the housing on the housing top opposite the handle.
- EP1415768 is the compact designed vibration damper disposed within a Tilgergephaseuses, which outside of the rest of the outer housing Hand tool on the handle opposite the housing top is releasably positively or non-positively fixed.
- the object of the invention is to reduce the overall length of a suitable for mounting in or on the power tool vibration damper.
- the total length of the vibration absorber is essentially determined by the absorber mass length. Since this is thus the largest possible, the smallest possible resonance frequencies can be achieved with a permanently specified absorber length and spring constants.
- Another advantage is that the internal pressure-biased spring duch the change of mass stops with respect to the vibration amplitude of the absorber mass performs only a half So Siemens spring stroke, as one of the two arranged on the outside, pressure-biased springs, whereby the spring itself is less stressed.
- the vibration absorber is mirror-symmetrical, whereby transverse vibrations are avoided.
- the absorber mass is arranged within a Tilgergephaseuses this at least a majority comprehensive, whereby this oscillatory subsystem is protected from contamination.
- the absorber mass is axially movably guided on Tilgergephaseuse, whereby this can oscillate freely up to Dämpfpe axially.
- the absorber housing per spring two axially spaced housing stops, where the spring is axially applied, whereby their position is limited axially on both sides.
- the Tilgergepuruse forms exactly two axially spaced housing stops for exactly one spring, which lie in the mirror plane, whereby the mirror symmetry is maintained.
- the absorber housing forms exactly four, in pairs axially spaced housing stops for exactly two springs, which lie in mirror image to the mirror plane, whereby the mirror symmetry is maintained.
- the absorber mass per spring two axially spaced mass stops from where the spring is axially applied, whereby the spring when swinging alternately applied to a respective mass stop and is pressure-clamped about it.
- the absorber mass is concave in the sector not enclosed by the absorber housing, whereby it is designed to fit a convex housing upper side of the outer housing of the portable power tool.
- the spring is arranged in a pocket-shaped, prismatic recess of the absorber mass, whereby it is at least partially constrained and thus can not break across under pressure threshold stress.
- the damper housing via fixing means such as screws non-positively and / or positively releasably fixed to the housing of the power tool, whereby the vibration damper, if necessary, by the user subsequently easily itself, for example.
- fixing means such as screws non-positively and / or positively releasably fixed to the housing of the power tool, whereby the vibration damper, if necessary, by the user subsequently easily itself, for example.
- To the outer casing of a vibration damper hand tool is mounted.
- FIG. 1 has a with respect to a striking axis A axially beating and rotating hand tool 1 a fixed along the striking axis A housing 2 Vibrationsstilger 3 with a vibratable absorber mass 4, which is axially biased by a spring 5 to the outer housing 2.
- the mirror plane S with the axis of impact A mirror-symmetrical vibration damper 3 is fixed via fastening means 6 in the form of screws on the housing 2 of the power tool 1 on the handle 7 opposite convex housing top 8 detachably fixed.
- the matching concave Tilgermasse 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) Tilgergephaseuse 9 and axially axially guided on this along the striking axis A extending guide surfaces 10.
- the spring 5 is arranged in a prismatic, in the plane of representation transversely to the impact axis A pocket-shaped, open end recess 11 of the absorber mass 4.
- Fig. 2 is formed as a helical compression spring spring 5 with respect to its axial spring length completely disposed within the absorber mass 4.
- the Tilgergephase 9 forms for exactly one spring 5 exactly two axially spaced housing stops 12, which lie in the mirror plane S.
- the absorber mass 4 forms at the end of the recess 11 two axially spaced mass stops 13, on which the spring 5 alternately bears against the oscillations (right and left field show different vibration states) under pressure.
- FIG. 3 and FIG. 4 forms the absorber housing 9 for the exact two springs 5 each two axially spaced housing stops 12, where the springs 5 are axially applied, which are mirror images of the mirror plane S.
- the housing stops 12 perpendicular to the mirror plane S inwardly from the absorber housing 9 a.
- Deviating collar after FIG. 5 and FIG. 6 the housing stops 12 for exactly two springs 5 parallel to the mirror plane S inwardly from the absorber housing 9 a.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Percussive Tools And Related Accessories (AREA)
- Vibration Prevention Devices (AREA)
- Auxiliary Devices For Machine Tools (AREA)
Abstract
Description
Die Erfindung bezeichnet einen Schwingungstilger für eine Handwerkzeugmaschine, insbesondere einen Bohrhammer, Kombihammer oder Meisselhammer.The invention refers to a vibration damper for a hand tool, in particular a hammer drill, combi hammer or chisel hammer.
Ein Schwingungstilger ist ein schwingungsfähiges Teilsystem, welches aus einer abstrakten schwingbaren Masse, einer abstrakten Feder und einem abstrakten Dämpfer besteht, welche jeweils nicht explizit als konkretes Bauteil ausgeführt sein müssen. Insbesondere der abstrakte Dämpfer wird oft nicht als konkretes Bauteil realisiert und ist dennoch durch praktisch stets auftretende Reib- und Strömungsverluste wirksam. Man unterscheidet gewöhnliche passive Schwingungstilger, welche ausschliesslich selbst erregt sind, von aktiv gesteuerten Schwingungstilgern.A vibration damper 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. In particular, the abstract damper is often not realized as a concrete component and is still effective by practically always occurring friction and flow losses. We differentiate ordinary passive vibration absorbers, which are exclusively self-excited, of actively controlled vibration absorbers.
Durch eine geeignete Wahl der Federkonstanten und der Masse wird bei einem passiven Schwingungstilger dessen Eigenfrequenz nahe der zu dämpfenden Störfrequenz dimensioniert, in diesem Verwendungsfall der Vibration des Aussengehäuses der Handwerkzeugmaschine.By a suitable choice of the spring constant and the mass of a passive vibration absorber whose natural frequency is dimensioned close to the noise frequency to be damped, in this case of use, the vibration of the outer housing of the power tool.
Nach der
Nach der
Nach der
Nach der
Nach der
Da die Gesamtlänge des Schwingungstilgers somit stets grösser als die Federlänge ist, wird zur Erzielung einer hinreichenden Schwingungsdämpfungswirkung ein relativ grosser, sich axial erstreckender Bauraum benötigt.Since the total length of the vibration absorber is thus always greater than the spring length, a relatively large, axially extending space is required to achieve a sufficient vibration damping effect.
Die Aufgabe der Erfindung besteht in der Reduzierung der Gesamtlänge eines zur Montage in oder an der Handwerkzeugmaschine geeigneten Schwingungstilgers.The object of the invention is to reduce the overall length of a suitable for mounting in or on the power tool vibration damper.
Die Aufgabe wird im Wesentlichen durch die Merkmale des Anspruchs 1 gelöst. Vorteilhafte Weiterbildungen ergeben sich aus den Unteransprüchen.The object is essentially achieved by the features of
So weist ein zur Montage an einem innenliegenden (bspw. Getriebedeckelgehäuse) oder aussenliegenden (bspw. Aussengehäuse) Gehäuse einer Handwerkzeugmaschine geeigneter Schwingungstilger eine schwingbare Tilgermasse auf, welche über zumindest eine Feder zum Gehäuse axial druckvorgespannt ist, wobei die Feder bezüglich ihrer axialen Federlänge vollständig innerhalb der Tilgermasse angeordnet ist.Thus, for mounting on an internal (eg gearbox housing) or external (eg outer housing) housing of a hand tool suitable vibration damper on a vibratable absorber mass, which is axially biased by at least one spring to the housing, the spring with respect to their axial spring length completely within the absorber mass is arranged.
Durch die Anordnung der Feder vollständig innerhalb der schwingbaren Tilgermasse wird die Gesamtlänge des Schwingungstilgers im Wesentlichen durch die Tilgermassenlänge bestimmt. Da diese somit grösstmöglichst ist, sind bei fest vorgegebener Tilgerlänge und Federkonstanten kleinstmöglichste Resonanzfrequenzen erzielbar. Ein weiterer Vorteil besteht darin, dass die innenliegende druckvorgespannte Feder duch den Wechsel der Massenanschläge bezüglich der Schwingungsamplitude der Tilgermasse nur einen halb solangen Federhub ausführt, wie eine der beiden aussenseitig angeordneten, druckvorgespannten Federn, wodurch die Feder selbst weniger beansprucht wird.Due to the arrangement of the spring completely within the oscillatable absorber mass, the total length of the vibration absorber is essentially determined by the absorber mass length. Since this is thus the largest possible, the smallest possible resonance frequencies can be achieved with a permanently specified absorber length and spring constants. Another advantage is that the internal pressure-biased spring duch the change of mass stops with respect to the vibration amplitude of the absorber mass performs only a half Solangen spring stroke, as one of the two arranged on the outside, pressure-biased springs, whereby the spring itself is less stressed.
Vorteilhaft ist der Schwingungstilger spiegelsymmetrisch ausgebildet, wodurch Querschwingungen vermieden werden.Advantageously, the vibration absorber is mirror-symmetrical, whereby transverse vibrations are avoided.
Vorteilhaft ist die Tilgermasse innerhalb eines diese zumindest mehrheitlich umfassenden Tilgergehäuses angeordnet, wodurch dieses schwingfähige Teilsystem vor Verschmutzung geschützt ist.Advantageously, the absorber mass is arranged within a Tilgergehäuses this at least a majority comprehensive, whereby this oscillatory subsystem is protected from contamination.
Vorteilhaft ist die Tilgermasse am Tilgergehäuse axial beweglich geführt, wodurch diese bis auf Dämpfverluste frei axial schwingen kann.Advantageously, the absorber mass is axially movably guided on Tilgergehäuse, whereby this can oscillate freely up to Dämpfverluste axially.
Vorteilhaft bildet das Tilgergehäuse je Feder zwei axial beabstandete Gehäuseanschläge aus, an denen die Feder axial anlegbar ist, wodurch deren Lage axial beidseitig begrenzt ist.Advantageously, the absorber housing per spring two axially spaced housing stops, where the spring is axially applied, whereby their position is limited axially on both sides.
Vorteilhaft bildet das Tilgergehäuse für genau eine Feder genau zwei axial beabstandete Gehäuseanschläge aus, die in der Spiegelebene liegen, wodurch die Spiegelsymmetrie erhalten bleibt.Advantageously, the Tilgergehäuse forms exactly two axially spaced housing stops for exactly one spring, which lie in the mirror plane, whereby the mirror symmetry is maintained.
Alternativ vorteilhaft bildet das Tilgergehäuse für genau zwei Federn genau vier, paarweise axial beabstandete Gehäuseanschläge aus, die spiegelbildlich zu der Spiegelebene liegen, wodurch die Spiegelsymmetrie erhalten bleibt.Alternatively advantageously, the absorber housing forms exactly four, in pairs axially spaced housing stops for exactly two springs, which lie in mirror image to the mirror plane, whereby the mirror symmetry is maintained.
Vorteilhaft bildet die Tilgermasse je Feder zwei axial beabstandete Massenanschläge aus, an denen die Feder axial anlegbar ist, wodurch die Feder beim Schwingen alternierend an je einem Massenanschlag anliegt und darüber druckverspannt wird.Advantageously, the absorber mass per spring two axially spaced mass stops from where the spring is axially applied, whereby the spring when swinging alternately applied to a respective mass stop and is pressure-clamped about it.
Vorteilhaft ist die Tilgermasse im nicht vom Tilgergehäuse umschlossenen Sektor konkav ausgebildet, wodurch diese passend zu einer konvexen Gehäuseoberseite des Aussengehäuses der Handwerkzeugmaschine ausgebildet ist.Advantageously, the absorber mass is concave in the sector not enclosed by the absorber housing, whereby it is designed to fit a convex housing upper side of the outer housing of the portable power tool.
Vorteilhaft ist die Feder in einer taschenförmigen, prismatischen Aussparung der Tilgermasse angeordnet, wodurch diese zumindest teilweise zwangsgeführt ist und somit bei Druckschwellbeanspruchung nicht quer ausbrechen kann.Advantageously, the spring is arranged in a pocket-shaped, prismatic recess of the absorber mass, whereby it is at least partially constrained and thus can not break across under pressure threshold stress.
Vorteilhaft ist das Tilgergehäuse über Festlegungsmittel wie bspw. Schrauben kraft- und/oder formschlüssig am Gehäuse der Handwerkzeugmaschine lösbar festgelegt, wodurch der Schwingungsdämpfer bedarfsweise vom Nutzer nachträglich leicht selbst bspw. zum Aussengehäuse einer schwingungstilgerfreien Handwerkzeugmaschine montierbar ist.Advantageously, the damper housing via fixing means such as screws non-positively and / or positively releasably fixed to the housing of the power tool, whereby the vibration damper, if necessary, by the user subsequently easily itself, for example. To the outer casing of a vibration damper hand tool is mounted.
Die Erfindung wird bezüglich eines vorteilhaften Ausführungsbeispiels näher erläutert mit:
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Fig. 1 als Schwingungstilger mit Handwerkzeugmaschine -
Fig. 2 als Längsschnitt -
Fig. 3 als Variante -
Fig. 4 als Längsschnitt der Variante -
Fig. 5 als weitere Variante -
Fig. 6 als Längsschnitt der weiteren Variante
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Fig. 1 as a vibration damper with hand tool -
Fig. 2 as a longitudinal section -
Fig. 3 as a variant -
Fig. 4 as a longitudinal section of the variant -
Fig. 5 as another variant -
Fig. 6 as a longitudinal section of the other variant
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Claims (11)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102007000057A DE102007000057B4 (en) | 2007-01-31 | 2007-01-31 | Vibration damper for hand tool |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1952952A2 true EP1952952A2 (en) | 2008-08-06 |
EP1952952A3 EP1952952A3 (en) | 2012-10-24 |
EP1952952B1 EP1952952B1 (en) | 2014-03-12 |
Family
ID=39223087
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08100762.7A Active EP1952952B1 (en) | 2007-01-31 | 2008-01-22 | Oscillation mass damper for hand tools |
Country Status (5)
Country | Link |
---|---|
US (1) | US8356702B2 (en) |
EP (1) | EP1952952B1 (en) |
JP (1) | JP5192246B2 (en) |
CN (1) | CN101235870B (en) |
DE (1) | DE102007000057B4 (en) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2018939A3 (en) * | 2007-07-24 | 2010-05-19 | Makita Corporation | Power tool with vibration damping mechanism |
EP2159008A3 (en) * | 2008-08-29 | 2011-03-23 | Makita Corporation | Impact tool |
WO2011072910A1 (en) * | 2009-12-16 | 2011-06-23 | Robert Bosch Gmbh | Handheld machine tool device |
DE102010041928A1 (en) | 2010-10-04 | 2012-04-05 | Robert Bosch Gmbh | Multidimensional vibration absorber |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102009014970A1 (en) | 2009-03-18 | 2010-09-23 | C. & E. Fein Gmbh | Oscillation tool with vibration damping |
EP2311358B1 (en) | 2009-10-19 | 2015-12-23 | Eurofilters Holding N.V. | Holding plate for a vacuum cleaner filter bag |
DE102009054723A1 (en) * | 2009-12-16 | 2011-06-22 | Robert Bosch GmbH, 70469 | Hand tool |
DE102010002262A1 (en) * | 2010-02-23 | 2011-08-25 | Robert Bosch GmbH, 70469 | External absorber |
DE102011007725A1 (en) * | 2011-04-20 | 2012-10-25 | Hilti Aktiengesellschaft | Hand tool and absorber |
US10232500B2 (en) * | 2012-12-17 | 2019-03-19 | Swerea Ivf Ab | Impact machine |
AU2015276285A1 (en) * | 2014-06-16 | 2017-01-19 | Swerea Ivf Ab | An impact machine |
CN215617869U (en) * | 2018-04-04 | 2022-01-25 | 米沃奇电动工具公司 | Rotary hammer suitable for applying axial impact to tool head |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE815179C (en) | 1949-11-17 | 1951-10-01 | Franz Dr-Ing Bollenrath | Pneumatic hammer with mass balancing |
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 |
US4478293A (en) | 1981-06-10 | 1984-10-23 | Hilti Aktiengesellschaft | Hammer drill or chipping hammer |
EP1415768A1 (en) | 2002-10-31 | 2004-05-06 | Atlas Copco Electric Tools GmbH | Oscillation damper |
WO2006022345A1 (en) | 2004-08-27 | 2006-03-02 | Makita Corporation | Working tool |
EP1710052A1 (en) | 2003-03-21 | 2006-10-11 | Black & Decker, Inc. | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
Family Cites Families (21)
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US1547774A (en) * | 1923-09-11 | 1925-07-28 | Ingersoll Rand Co | Handle for percussive tools |
US1874039A (en) * | 1926-11-26 | 1932-08-30 | Packard Motor Car Co | Internal combustion engine |
US1845825A (en) * | 1927-07-22 | 1932-02-16 | Chicago Pneumatic Tool Co | Spring handle attachment for rock drills |
US3525887A (en) * | 1968-08-16 | 1970-08-25 | Benjamin B D Ewart Jr | Motor with linear reciprocating output |
US3845827A (en) * | 1971-08-05 | 1974-11-05 | Stihl Maschf Andreas | Portable implement,especially motor chain saw |
DE2403074C3 (en) * | 1974-01-23 | 1978-10-26 | Demag Ag, 4100 Duisburg | Pneumatic impact tool |
JPS52135401U (en) * | 1976-04-08 | 1977-10-14 | ||
US4238104A (en) * | 1978-08-14 | 1980-12-09 | Rex Hamilton | Energy absorbing motor mount assembly |
US4991698A (en) * | 1988-05-16 | 1991-02-12 | Bose Corporation | Damping with damping mass inside wheel |
SE469549B (en) * | 1991-11-04 | 1993-07-26 | Atlas Copco Tools Ab | VIBRATION-INJURY BODY FOR A MANUFACTURED TOOL |
US5471969A (en) * | 1993-09-28 | 1995-12-05 | Mcdonald, Jr.; Norman J. | Stabilizers adapted to be connected to a bow |
DE19524948A1 (en) * | 1994-07-30 | 1996-02-01 | Volkswagen Ag | Automotive exhaust vibration damper |
JPH10138727A (en) * | 1996-11-14 | 1998-05-26 | Nissan Motor Co Ltd | Suspension structure |
US6364078B1 (en) * | 1998-08-27 | 2002-04-02 | Bose Corporation | Wheel damping |
ITBS20040008U1 (en) * | 2004-02-12 | 2004-05-12 | Cropelli S R L | INTIVIBRATING COMPASS FOR CANNON POINTS |
EP1618999B1 (en) * | 2004-07-14 | 2008-06-25 | AEG Electric Tools GmbH | Hand held percussive tool or drill |
JP4920900B2 (en) * | 2004-07-15 | 2012-04-18 | 株式会社マキタ | Anti-vibration handle |
JP4509698B2 (en) * | 2004-08-27 | 2010-07-21 | 株式会社マキタ | Work tools |
GB2429675A (en) * | 2005-06-23 | 2007-03-07 | Black & Decker Inc | Vibration dampening mechanism |
DE102007000056A1 (en) * | 2007-01-31 | 2008-09-18 | Hilti Aktiengesellschaft | Vibration damper for hand tool |
US7806201B2 (en) * | 2007-07-24 | 2010-10-05 | Makita Corporation | Power tool with dynamic vibration damping |
-
2007
- 2007-01-31 DE DE102007000057A patent/DE102007000057B4/en not_active Expired - Fee Related
-
2008
- 2008-01-22 EP EP08100762.7A patent/EP1952952B1/en active Active
- 2008-01-29 JP JP2008017518A patent/JP5192246B2/en not_active Expired - Fee Related
- 2008-01-29 CN CN200810004914XA patent/CN101235870B/en active Active
- 2008-01-30 US US12/012,056 patent/US8356702B2/en active Active
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE815179C (en) | 1949-11-17 | 1951-10-01 | Franz Dr-Ing Bollenrath | Pneumatic hammer with mass balancing |
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 |
US4478293A (en) | 1981-06-10 | 1984-10-23 | Hilti Aktiengesellschaft | Hammer drill or chipping hammer |
EP1415768A1 (en) | 2002-10-31 | 2004-05-06 | Atlas Copco Electric Tools GmbH | Oscillation damper |
EP1710052A1 (en) | 2003-03-21 | 2006-10-11 | Black & Decker, Inc. | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
WO2006022345A1 (en) | 2004-08-27 | 2006-03-02 | Makita Corporation | Working tool |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2018939A3 (en) * | 2007-07-24 | 2010-05-19 | Makita Corporation | Power tool with vibration damping mechanism |
US7806201B2 (en) | 2007-07-24 | 2010-10-05 | Makita Corporation | Power tool with dynamic vibration damping |
EP2159008A3 (en) * | 2008-08-29 | 2011-03-23 | Makita Corporation | Impact tool |
US7967078B2 (en) | 2008-08-29 | 2011-06-28 | Makita Corporation | Impact tool |
WO2011072910A1 (en) * | 2009-12-16 | 2011-06-23 | Robert Bosch Gmbh | Handheld machine tool device |
DE102010041928A1 (en) | 2010-10-04 | 2012-04-05 | Robert Bosch Gmbh | Multidimensional vibration absorber |
WO2012045504A1 (en) | 2010-10-04 | 2012-04-12 | Robert Bosch Gmbh | Multidimensional vibration damper |
Also Published As
Publication number | Publication date |
---|---|
DE102007000057A1 (en) | 2008-08-14 |
EP1952952A3 (en) | 2012-10-24 |
DE102007000057B4 (en) | 2010-07-08 |
JP2008188759A (en) | 2008-08-21 |
CN101235870A (en) | 2008-08-06 |
US8356702B2 (en) | 2013-01-22 |
EP1952952B1 (en) | 2014-03-12 |
JP5192246B2 (en) | 2013-05-08 |
US20080179797A1 (en) | 2008-07-31 |
CN101235870B (en) | 2012-04-18 |
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