EP2127821A1 - Electric tool with vibration dampener - Google Patents
Electric tool with vibration dampener Download PDFInfo
- Publication number
- EP2127821A1 EP2127821A1 EP08009603A EP08009603A EP2127821A1 EP 2127821 A1 EP2127821 A1 EP 2127821A1 EP 08009603 A EP08009603 A EP 08009603A EP 08009603 A EP08009603 A EP 08009603A EP 2127821 A1 EP2127821 A1 EP 2127821A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- power tool
- mass
- elements
- axis
- guide means
- 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
- 230000005540 biological transmission Effects 0.000 claims abstract description 21
- 239000006096 absorbing agent Substances 0.000 claims description 30
- 230000003534 oscillatory effect Effects 0.000 claims description 26
- 230000005484 gravity Effects 0.000 claims description 9
- 229910000831 Steel Inorganic materials 0.000 claims description 2
- 239000010959 steel Substances 0.000 claims description 2
- 125000006850 spacer group Chemical group 0.000 description 10
- 238000013016 damping Methods 0.000 description 6
- 238000009527 percussion Methods 0.000 description 6
- 230000005284 excitation Effects 0.000 description 2
- 230000002349 favourable effect Effects 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000010355 oscillation Effects 0.000 description 2
- 230000007704 transition Effects 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 230000002238 attenuated effect Effects 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 150000002739 metals Chemical class 0.000 description 1
Images
Classifications
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- 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
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- 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
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- 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
Definitions
- the invention relates to a power tool, in particular a hammer drill, comprising an electric motor with a rotation axis, a transmission gear and a striking mechanism with a striking axis, wherein the striking mechanism is driven by the electric motor via the transmission gear.
- the power tool comprises a vibration damper with a vibratory mass.
- Power tools in the operation of blows, for example, by a percussion, on an object, such as a building wall or a ceiling exerted, generate by the impact of strokes significant kickback forces to be absorbed by the user of the power tool.
- kickback forces there are several approaches.
- a vibration damper on the power tool, which is formed in principle by an oscillatory mass which is mounted in a guide or freely in or on the housing of the power tool.
- the oscillatory mass is held by an elastic element, which is usually a spring, for example a coil spring.
- the mass of the oscillatory mass as well as the spring constant of the elastic element are preferably adjusted such that the system of the oscillating and spring-mounted mass has a natural or resonant frequency in the vicinity of the typical excitation frequency by the percussion (excitation frequency).
- the European patent application EP 1 736 283 A2 shows such a vibration absorber, which is arranged at horizontal orientation of the hammer drill above the striking axis.
- the vibration damper shown here has the disadvantage that it is limited because of its respect to the largest possible mass of the oscillatory mass, because the arrangement of the oscillatory mass above the striking axis limited a certain size of the oscillatory mass, if not the housing of the hammer accordingly extended, ie should be enlarged.
- the vibration absorber disclosed in this document is limited to a single oscillatory mass so that all the vibrational energy is substantially transmitted through a single element. This has disadvantages for the mounting of the oscillatory mass, which is correspondingly more stable to perform.
- Object of the present invention is therefore to construct a power tool with a vibration damper, the arrangement and design is more efficient and more compact than the known solutions.
- the oscillatory mass has at least two separate mass elements which are arranged in a common half-space with an interface extending parallel to the striking axis and containing the striking axis.
- a power tool is provided which comprises an efficient and securely mounted vibration absorber.
- the oscillatory mass is formed from at least two separate mass elements, it is particularly well possible to achieve a distribution of the oscillatory mass to a particularly favorable range on the power tool.
- the arrangement according to the invention of the mass elements in a common half-space with an interface extending parallel to the impact axis makes use of favorable attachment possibilities.
- the mass elements of a hammer drill which is in an upright position, ie with a substantially horizontally oriented impact axis and downwardly protruding main grip part, both may be arranged below the striking axis.
- the interface is in this example a substantially horizontally extending plane, below or above which the at least two separate mass elements can be arranged. Accordingly, since the striking axis is not located directly between the mass elements of the oscillatory mass, that is, the mass elements do not surround the striking axis, the diameter of the housing surrounding the striking axis need not be additionally increased.
- the vibration damper is arranged in the direction of force flow (at an interface) between the electric motor and the transmission gear.
- the arrangement of the vibration absorber in such a region also makes it possible that the oscillatory mass is arranged in a central region of the power tool.
- Such an arrangement point is advantageous for the vibration absorber because it is arranged here in the vicinity of the center of gravity of the power tool and thus can reduce center-of-gravity vibrations particularly efficiently.
- the axis of rotation of the electric motor and the striking axis of the impact mechanism are arranged at a non-zero angle to each other, wherein the angle is preferably in an angular range between 80 ° and 100 °.
- Such a design of the power tool allows a particularly simple arrangement of the oscillatory mass in a common half-space, because the power tool in this case has a larger dimension perpendicular to the striking axis than in the case of a power tool, in which the axis of rotation of the electric motor and the striking axis of the percussion parallel to each other, in particular aligned (in-line arrangement).
- the transmission gear is located substantially away from the striking axis of the impact mechanism.
- the transmission gear or an area in which the force is transferred from the electric motor to the transmission gear is particularly well suited for the arrangement of the vibration absorber according to the invention, because here the thickness (depth) of the power tool is particularly small, ie the recorded in the outer housing Apply components little, and thus a good opportunity exists to arrange the oscillating mass elements in this area, without the diameter of the outer housing is to increase significantly.
- the transmission gear is located substantially in a region of the center of gravity of the power tool.
- the range of the transmission gear or its transition region is particularly well suited for the arrangement of the oscillatory mass. If the transmission transmission is located substantially in a region of the center of gravity of the power tool, therefore, the vibration damper can be particularly easily arranged in the region of the center of gravity of the power tool.
- the arrangement of the vibration absorber in the region of the center of gravity always has the advantage that, in particular, center-of-mass vibrations of the power tool can be efficiently damped or canceled out.
- the distance between the striking axis and the vibration damper in a range of 60 mm to 90 mm. This distance between the vibration absorber and the striking axis allows a particularly efficient damping of the vibrations of the power tool, at the same time an arrangement of the vibration absorber off the striking axis is easily possible.
- the mass elements of the vibration absorber along exactly one orientation are movable and each have a rest position, wherein the mass elements are acted upon in a deflection from the respective rest position with a counter to the deflection spring force.
- the orientation in which the mass elements of the vibration absorber can move may preferably correspond to the orientation of the striking axis, so that the vibrations resulting from impacts along the striking axis can be specifically damped or eliminated by the mass elements.
- the fact that the mass elements are movable along exactly one orientation for example guided by a guide shaft, enables the vibration damper to selectively dampen certain vibrations and impacts. It is there too possible that different mass elements are movable in different orientations.
- the mass elements are preferably applied during any movement from the rest position with a spring force in the direction of the rest position. This means that even small deflections of the mass elements can produce a good vibration damping.
- the rest position can be defined in such a way that here the spring forces acting on the respective mass element cancel each other out.
- the orientation of the mass elements is defined by a respective guide device, wherein the guide means are spaced perpendicular to the alignment.
- guide means can serve here, for example, a rod guide on which one of the mass elements along the bar direction can slide.
- the guide means are preferably aligned parallel to each other and perpendicular to this orientation horizontally and / or vertically spaced. They can thus be arranged on one side of the impact axis within the same half-space, so that a balanced vibration damping on both sides of the impact axis of a half-space is made possible.
- the guide means are integrally formed with each other and with a spacing device, and in particular the guide means and the spacing means are designed as parts of a frame element. That is, the guide means and the spacer means together form a component which can be attached to a power tool.
- the frame element is designed such that the guide means form substantially two opposite sides of a rectangle and the spacer means are formed by two substantially perpendicular to the guide means extending spacers as two more opposite sides of the rectangle.
- the spacer means are formed by two substantially perpendicular to the guide means extending spacers as two more opposite sides of the rectangle.
- a rectangle having four sides is formed by two pairwise opposing spacing and guiding devices.
- the guide means and the spacing means are substantially parallel to each other and form the rectangular frame.
- the mass elements each consist of two Partemementen, wherein the sub-elements of the mass elements are acted upon in particular with counteracting spring forces against each other. Since the sub-elements are acted upon against each other with spring forces, they have a movement characteristic of a single mass element.
- the sub-elements are screwed together, joined or glued, with an application of spring forces makes such a connection of the individual sub-elements superfluous, whereby the assembly of the vibration absorber is facilitated and thus favored.
- the mass of the oscillatory mass of the vibration absorber is 5% to 10% of the mass of the power tool.
- Such a choice of the total mass of the oscillatory mass of the vibration absorber allows efficient vibration damping, without the power tool is made unnecessarily heavier by the additional mass.
- the oscillatory mass of the vibration damper includes sintered steel. But there are others Materials, preferably metals, for use as a vibratory mass possible.
- the power tool according to the invention has the advantage that the oscillatory mass of the vibration damper is designed and arranged in a particularly efficient and space-saving manner.
- the power tool according to the invention is thus much more comfortable to use for a user, since a large proportion of the resulting during operation of the power tool vibrations is attenuated by the vibration absorber and the power tool is still easy to handle.
- Such an active reduction of the vibration, as achieved by a vibration absorber may amount to at least 30% of the total vibration energy.
- the vibration damping in a power tool according to the invention can preferably be further improved by passive devices, such as spring-loaded handles.
- Fig. 1 shows a power tool 10 with an electric motor 40 having a substantially vertically oriented axis of rotation Ax2, a percussion 50, with a substantially horizontally oriented impact axis Ax1 and a transition gear 60, via which the impactor 50 is driven by the electric motor 40.
- Fig. 1 In this case, only the positions of the electric motor 40, the percussion mechanism 50 and the transmission gear 60 are shown, wherein the said elements are each arranged behind a cover of the housing of the power tool 10 and are not visible from the outside.
- the power tool 10 comprises a vibration damper 12, which is arranged between the electric motor 40 and the transmission gear 60. Since the transmission gear 60, and the electric motor 40 are each housed in a gear or motor housings, the vibration damper 12 is at this position from an influence by oil, which can be separated, for example, from the transmission gear 60, separated.
- the arrangement of the vibration damper 12 is chosen so that the vibration damper 12 is located substantially in a region of the center of gravity of the power tool 10.
- the center of gravity of the power tool 10 is located below the impact axis Ax1 of the impact mechanism 50 and lies substantially on the axis of rotation Ax2 of the electric motor 40th
- the vibration damper 12 incidentally in the FIGS. 3 to 5 is described in more detail, has a mass element 14L, which is composed of two mass parts 14.1, 14.2 and along a guide device 18.1, 18.2 in exactly one orientation A1 (damped) is capable of oscillation.
- the orientation A1, in which the mass element 14L can oscillate, is aligned parallel to the orientation of the impact axis Ax1 of the striking mechanism 50.
- the mass member 14L is able to vibrate along the orientation of the striking axis Ax1 and thus makes it possible to efficiently damp vibrations and impacts acting along the striking axis Ax1.
- the oscillation of the mass element 14L is also made possible by two spring elements 16.1, 16.2, which each exert a spring force on the mass element 14L.
- the spring forces of the spring elements 16.1, 16.2 are directed against each other, so that the mass element 14L is without the influence of additional external forces in a rest position in which the two spring elements 16.1, 16.2 are compressed substantially equal, so that the spring elements 16.1, 16.2 opposite equal large forces on the mass element 14L exercise.
- Fig. 2 shows the power tool 10 off Fig. 1 in a front view, where Fig. 2 additionally shows an interface HR, in which the impact axis Ax1 of the impact mechanism 50 is located, and which is extended substantially horizontally in the upright position of the power tool 10.
- the interface HR divides the space in which the power tool 10 is located in two half-spaces, namely an upper half-space 30 and a lower half-space 20.
- the upper half-space 30 contains everything that is above the interface HR, whereas the lower half space 20 contains all the elements located below (and inside) the interface HR.
- Fig. 2 shows that the vibration absorber 12 has two mass elements 14L, 14R arranged on both sides of the striking axis Ax1 and in the lower half space 20.
- the two mass elements 14L, 14R are by a perpendicular to the impact axis Ax1 and substantially horizontally extending spacer 22.1 spaced apart and interconnected.
- Fig. 3 shows a vibration damper 12 in a plan view.
- illustrated illustration of the vibration absorber 12 shows the two mass elements 14L, 14R, which are each composed of two sub-elements 14.1 ... 14.4.
- the sub-elements 14.1 ... 14.4 each form a half mass element 14L, 14R and are not glued together, screwed or joined together in the embodiment shown here.
- the two sub-elements 14.1, 14.2 and 14.3, 14.4 are pressed against each other by two spring elements 16.1, 16.2 and 16.3, 16.4.
- the spring elements 16.1 ... 16.4 each exert a force on the sub-elements 14.1 ...
- Mass elements 14L, 14R lie in a rest position.
- the rest position, in which the mass elements 14L, 14R lie, results from the embodiments of the spring elements 16.1 ... 16.4 and is where the spring forces of the spring elements 16.1, 16.2 or 16.3, 16.4 opposite are the same size.
- the vibration damper 12 includes guide means 18.2, 18.4 (further guide means 18.1, 18.3 are in the FIGS. 1 . 4 and 5 to be recognized), wherein the guide means 18.2, 18.4 are each aligned along exactly one orientation A1, A2.
- the alignments A1, A2 are parallel to each other and in the installed state and horizontally spaced in the upright position of the power tool 10.
- the mass elements 14L, 14R are supported in such a way that they respectively enclose the guide device 18.2, 18.4 (and 18.1, 18.3), which are each designed as pins.
- the guide means 18.2, 18.4 are spaced apart in the embodiment shown here by two spacer elements 22.1, 22.2.
- the guide means 18.2, 18.4 and the spacer elements 22.1, 22.2 together form a recognizable in plan view, substantially rectangular frame, so that the mass elements 14L, 14R along fixed and mutually coupled alignments A1, A2 are capable of oscillating.
- fastening means in the form of eyelets 24.1 ... 24.4 are also provided, with which the vibration damper 12 can be attached to the power tool 10.
- Fig. 4 shows the vibration damper 12 Fig. 3 in a side view and as a sectional view. Fig. 4 Therefore, it is possible to describe the arrangement of the subelements 14.1, 14.2 of a mass element 14L on the guide devices 18.1, 18.2 of the vibration absorber 12.
- Fig. 4 shows clearly that the guide means 18.1, 18.2, which are vertically spaced from each other and aligned parallel to each other, are designed as guide pins.
- the guide devices 18.1, 18.2 in this case run continuously between the first spacer element 22.1 and the second spacer element 22.2.
- the sub-elements 14.1, 14.2 of the mass element 14L each have two holes through which the guide devices 18.1, 18.2 extend.
- the holes in the sub-elements 14.1, 14.2 are designed and aligned such that the Sub-elements 14.1, 14.2 on the guide means 18.1, 18.2, which are designed as pins, are displaceable.
- the sub-elements 14.1, 14.2 of the mass element 14L each have a recess into which in each case a spring element 16.1, 16.2 extends.
- the spring elements 16.1, 16.2 are therefore clamped between in each case a spacer element 22.1, 22.2 and in each case one partial element 14.1, 14.2 and act upon the partial elements 14.1, 14.2 with a force.
- the forces exerted by the spring elements 16.1, 16.2 on the sub-elements 14.1, 14.2, are directed against each other.
- the mass element 14L which is formed from the sub-elements 14.1, 14.2, is in a rest position, provided that the forces of the spring elements 16.1, 16.2 are opposite in size equal.
- the application of a spring force of the mass member 14L makes it possible to vibrate the mass member 14L at an externally applied accelerating force.
- a natural or resonant frequency of the vibration absorber 12 is equal to a typical vibration frequency, which is transmitted by the impact mechanism 50 to the power tool 10.
- Fig. 5 shows a perspective view of the vibration absorber 12 from the FIGS. 3 and 4 , In this view, the arrangement of the previously described elements of the vibration absorber is clearly visible.
- the guide elements 18.1 ... 18.4, the arrangement of the mass elements 14L, 14R and the arrangement of the spring elements 16.1 ... 16.4 clearly.
- Fig. 5 shows that each two guide means 18.1, 18.2 and 18.3, 18.4 are designed as substantially horizontally extending pins.
- each of the guide elements 18.1, 18.2 and 18.2, 18.4 form a pair that guides a mass element 14L, 14R in a horizontal orientation.
- Each of the mass elements 14L, 14R is composed of two subelements 14.1, 14.2 or 14.3, 14.4 as described above.
- the sub-elements 14.1, 14.2 and 14.3, 14.4 are held together as described by the spring elements 16.1 ... 16.4.
- two of the sub-elements 14.1, 14.3 hold at the middle height of the respective other sub-element 14.2, 14.4 side facing a notch, which is filled by a corresponding projection in the other sub-element 14.2, 14.4.
- the two sub-elements 14.1, 14.2 and 14.3, 14.4 held together on the one hand by the spring elements 16.1, 16.2 or 16.3, 16.4 and on the other hand by the nut and spring-like connection described above. Further fastening means of the sub-elements 14.1, 14.2 or 14.3, 14.4 are not provided here, but may additionally be present.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Percussive Tools And Related Accessories (AREA)
Abstract
Description
Die Erfindung betrifft ein Elektrowerkzeug, insbesondere einen Bohrhammer, umfassend einen Elektromotor mit einer Drehachse, ein Übertragungsgetriebe und ein Schlagwerk mit einer Schlagachse, wobei das Schlagwerk vom Elektromotor über das Übertragungsgetriebe angetrieben wird. Ferner umfasst das Elektrowerkzeug einen Schwingungstilger mit einer schwingungsfähigen Masse.The invention relates to a power tool, in particular a hammer drill, comprising an electric motor with a rotation axis, a transmission gear and a striking mechanism with a striking axis, wherein the striking mechanism is driven by the electric motor via the transmission gear. Furthermore, the power tool comprises a vibration damper with a vibratory mass.
Elektrowerkzeuge, bei deren Betrieb Schläge, beispielsweise durch ein Schlagwerk, auf ein Objekt, wie beispielsweise eine Gebäudewand oder eine Zimmerdecke, ausgeübt werden, erzeugen durch die vom Schlagwerk ausgeübten Schläge erhebliche Rückschlagkräfte, die von dem Benutzer des Elektrowerkzeugs aufzunehmen sind. Um die durch die Rückschlagkräfte erzeugten Vibrationen zu dämpfen, gibt es verschiedene Ansätze.Power tools, in the operation of blows, for example, by a percussion, on an object, such as a building wall or a ceiling exerted, generate by the impact of strokes significant kickback forces to be absorbed by the user of the power tool. To dampen the vibrations generated by the kickback forces, there are several approaches.
Eine Möglichkeit besteht darin, die Griffelemente, mit denen das Elektrowerkzeug gehalten wird, durch geeignete Maßnahmen zu dämpfen, d.h. einen Schwingungsdämpfer vorzusehen. Eine andere Möglichkeit beruht darauf, einen Schwingungstilger an dem Elektrowerkzeug vorzusehen, der prinzipiell durch eine schwingungsfähige Masse gebildet wird, die in einer Führung oder frei in oder an dem Gehäuse des Elektrowerkzeugs befestigt ist. Die schwingungsfähige Masse wird dabei durch ein elastisches Element gehalten, das üblicherweise eine Feder, beispielsweise eine Spiralfeder, ist. Die Masse der schwingungsfähigen Masse sowie die Federkonstante des elastischen Elements werden dabei bevorzugt derart eingestellt, dass das System der schwingenden und gefedert gelagerten Masse eine Eigen- oder Resonanzfrequenz in der Nähe der typischen Anregungsfrequenz durch das Schlagwerk (Erregerfrequenz) aufweist. Auf diese Weise wird durch das Schlagwerk eine besonders große Auslenkung der schwingungsfähigen Masse erzeugt, die somit einen großen Teil der Vibrationsenergie, die durch das Schlagwerk auf das Elektrowerkzeug übertragen wird, aufnehmen kann. Durch einen solchen Schwingungstilger ist es also möglich, einen Teil der Vibrationsenergie in eine Schwingung der schwingungsfähigen Masse zu übertragen und den Benutzer damit hinsichtlich der Vibrationen des Elektrowerkzeugs zu schonen.One possibility is to dampen the handle elements with which the power tool is held by suitable measures, ie to provide a vibration damper. Another possibility is based on providing a vibration damper on the power tool, which is formed in principle by an oscillatory mass which is mounted in a guide or freely in or on the housing of the power tool. The oscillatory mass is held by an elastic element, which is usually a spring, for example a coil spring. The mass of the oscillatory mass as well as the spring constant of the elastic element are preferably adjusted such that the system of the oscillating and spring-mounted mass has a natural or resonant frequency in the vicinity of the typical excitation frequency by the percussion (excitation frequency). In this way, a particularly large deflection of the oscillatory mass is generated by the impact mechanism, which thus can absorb a large part of the vibration energy that is transmitted by the percussion on the power tool. By such a vibration absorber, it is thus possible to transmit a portion of the vibration energy in a vibration of the oscillatory mass and thus protect the user with respect to the vibrations of the power tool.
Die europäische Patentanmeldung
Aufgabe der vorliegenden Erfindung ist es demnach, ein Elektrowerkzeug mit einem Schwingungstilger zu konstruieren, dessen Anordnung und Ausgestaltung effizienter und kompakter ist als die bekannten Lösungen.Object of the present invention is therefore to construct a power tool with a vibration damper, the arrangement and design is more efficient and more compact than the known solutions.
Die Lösung der Aufgabe wird durch die Merkmale des Anspruchs 1 erzielt. Erfindungsgemäß weist die schwingungsfähige Masse zumindest zwei separate Massenelemente auf, die in einem gemeinsamen Halbraum mit einer parallel zur Schlagachse verlaufenden und die Schlagachse enthaltenden Grenzfläche angeordnet sind. Durch die erfindungsgemäße Ausgestaltung der schwingungsfähigen Masse und deren Anordnung wird ein Elektrowerkzeug geschaffen, das einen effizienten und sicher befestigten Schwingungstilger umfasst. Indem die schwingungsfähigen Masse aus zumindest zwei separaten Massenelementen gebildet wird, ist es besonders gut möglich, eine Verteilung der schwingungsfähigen Masse auf einen besonders günstigen Bereich am Elektrowerkzeug zu erzielen. Die erfindungsgemäße Anordnung der Massenelemente in einem gemeinsamen Halbraum mit einer parallel zur Schlagachse verlaufenden Grenzfläche macht sich günstige Befestigungsmöglichkeiten zunutze. Beispielsweise können die Massenelemente eines Bohrhammers, der sich in einer aufrechten Position befindet, also mit im Wesentlichen horizontal ausgerichteter Schlagachse und nach unten vorstehendem Hauptgriffteil, beide unterhalb der Schlagachse angeordnet sein. Die Grenzfläche ist in diesem Beispiel eine sich im Wesentlichen horizontal erstreckende Ebene, unterhalb oder oberhalb der die zumindest zwei separaten Massenelemente angeordnet werden können. Da sich demnach die Schlagachse nicht unmittelbar zwischen den Massenelementen der schwingungsfähigen Masse befindet, die Massenelemente die Schlagachse also nicht umgeben, muss der Durchmesser des die Schlagachse umgebenden Gehäuses nicht zusätzlich vergrößert werden.The solution of the problem is achieved by the features of claim 1. According to the invention, the oscillatory mass has at least two separate mass elements which are arranged in a common half-space with an interface extending parallel to the striking axis and containing the striking axis. The inventive design of the oscillatory mass and its arrangement, a power tool is provided which comprises an efficient and securely mounted vibration absorber. By the oscillatory mass is formed from at least two separate mass elements, it is particularly well possible to achieve a distribution of the oscillatory mass to a particularly favorable range on the power tool. The arrangement according to the invention of the mass elements in a common half-space with an interface extending parallel to the impact axis makes use of favorable attachment possibilities. For example, the mass elements of a hammer drill, which is in an upright position, ie with a substantially horizontally oriented impact axis and downwardly protruding main grip part, both may be arranged below the striking axis. The interface is in this example a substantially horizontally extending plane, below or above which the at least two separate mass elements can be arranged. Accordingly, since the striking axis is not located directly between the mass elements of the oscillatory mass, that is, the mass elements do not surround the striking axis, the diameter of the housing surrounding the striking axis need not be additionally increased.
Bevorzugt ist der Schwingungstilger in Kraftflussrichtung (an einer Schnittstelle) zwischen dem Elektromotor und dem Übertragungsgetriebe angeordnet. Die Anordnung des Schwingungstilgers in einem solchen Bereich ermöglicht es zudem, dass die schwingungsfähige Masse in einem zentralen Bereich des Elektrowerkzeugs angeordnet wird. Ein solcher Anordnungspunkt ist für den Schwingungstilger deshalb von Vorteil, weil er hier in der Nähe des Schwerpunkts des Elektrowerkzeugs angeordnet ist und somit Schwerpunktsvibrationen besonders effizient vermindern kann.Preferably, the vibration damper is arranged in the direction of force flow (at an interface) between the electric motor and the transmission gear. The arrangement of the vibration absorber in such a region also makes it possible that the oscillatory mass is arranged in a central region of the power tool. Such an arrangement point is advantageous for the vibration absorber because it is arranged here in the vicinity of the center of gravity of the power tool and thus can reduce center-of-gravity vibrations particularly efficiently.
Vorteilhafterweise sind die Drehachse des Elektromotors und die Schlagachse des Schlagwerks unter einem von Null verschiedenen Winkel zueinander angeordnet, wobei der Winkel bevorzugt in einem Winkelbereich zwischen 80° und 100° liegt. Eine derartige Ausgestaltung des Elektrowerkzeugs ermöglicht eine besonders einfache Anordnung der schwingungsfähigen Masse in einem gemeinsamen Halbraum, weil das Elektrowerkzeug in diesem Fall eine größere Dimension senkrecht zur Schlagachse aufweist als im Fall eines Elektrowerkzeugs, bei dem die Drehachse des Elektromotors und die Schlagachse des Schlagwerks parallel zu einander, insbesondere fluchtend angeordnet sind (In-Line Anordnung).Advantageously, the axis of rotation of the electric motor and the striking axis of the impact mechanism are arranged at a non-zero angle to each other, wherein the angle is preferably in an angular range between 80 ° and 100 °. Such a design of the power tool allows a particularly simple arrangement of the oscillatory mass in a common half-space, because the power tool in this case has a larger dimension perpendicular to the striking axis than in the case of a power tool, in which the axis of rotation of the electric motor and the striking axis of the percussion parallel to each other, in particular aligned (in-line arrangement).
In einer weiteren bevorzugten Ausführungsform liegt das Übertragungsgetriebe im Wesentlichen abseits der Schlagachse des Schlagwerks. Das Übertragungsgetriebe bzw. ein Bereich, in dem die Kraft von dem Elektromotor auf das Übertragungsgetriebe überführt wird, eignet sich besonders gut für die Anordnung des erfindungsgemäßen Schwingungstilgers, weil hier die Dicke (Tiefe) des Elektrowerkzeugs besonders klein ist, d.h. die in dem Außengehäuse aufgenommenen Bauteile wenig auftragen, und somit eine gute Möglichkeit dafür besteht, die schwingenden Massenelemente in diesem Bereich anzuordnen, ohne dass der Durchmesser des Außengehäuses merklich zu vergrößern ist.In a further preferred embodiment, the transmission gear is located substantially away from the striking axis of the impact mechanism. The transmission gear or an area in which the force is transferred from the electric motor to the transmission gear, is particularly well suited for the arrangement of the vibration absorber according to the invention, because here the thickness (depth) of the power tool is particularly small, ie the recorded in the outer housing Apply components little, and thus a good opportunity exists to arrange the oscillating mass elements in this area, without the diameter of the outer housing is to increase significantly.
Vorteilhafterweise befindet sich das Übertragungsgetriebe im Wesentlichen in einem Bereich des Schwerpunkts des Elektrowerkzeugs. Wie oben beschrieben, eignet sich der Bereich des Übertragungsgetriebes bzw. dessen Übergangsbereich besonders gut für die Anordnung der schwingungsfähigen Masse. Sofern das Übertragungsgetriebe im Wesentlichen in einem Bereich des Schwerpunkts des Elektrowerkzeugs liegt, kann daher auch der Schwingungstilger besonders leicht im Bereich des Schwerpunkts des Elektrowerkzeugs angeordnet werden. Wie oben beschrieben, hat die Anordnung des Schwingungstilgers im Bereich des Schwerpunkts in jedem Fall den Vorteil, dass insbesondere Schwerpunktsvibrationen des Elektrowerkzeugs effizient gedämpft bzw. getilgt werden können. Mit Vorteil liegt der Abstand zwischen der Schlagachse und dem Schwingungstilger in einem Bereich von 60 mm bis 90 mm. Dieser Abstand zwischen dem Schwingungstilger und der Schlagachse ermöglicht eine besonders effiziente Dämpfung der Vibrationen des Elektrowerkzeugs, wobei gleichzeitig eine Anordnung des Schwingungstilgers abseits der Schlagachse leicht ermöglicht wird.Advantageously, the transmission gear is located substantially in a region of the center of gravity of the power tool. As described above, the range of the transmission gear or its transition region is particularly well suited for the arrangement of the oscillatory mass. If the transmission transmission is located substantially in a region of the center of gravity of the power tool, therefore, the vibration damper can be particularly easily arranged in the region of the center of gravity of the power tool. As described above, the arrangement of the vibration absorber in the region of the center of gravity always has the advantage that, in particular, center-of-mass vibrations of the power tool can be efficiently damped or canceled out. Advantageously, the distance between the striking axis and the vibration damper in a range of 60 mm to 90 mm. This distance between the vibration absorber and the striking axis allows a particularly efficient damping of the vibrations of the power tool, at the same time an arrangement of the vibration absorber off the striking axis is easily possible.
Bevorzugt sind die Massenelemente des Schwingungstilgers entlang genau einer Ausrichtung beweglich und weisen je eine Ruhelage auf, wobei die Massenelemente bei einer Auslenkung aus der jeweiligen Ruhelage mit einer entgegen der Auslenkung wirkenden Federkraft beaufschlagt sind. Die Ausrichtung, in welcher sich die Massenelemente des Schwingungstilgers bewegen können, kann dabei bevorzugt der Ausrichtung der Schlagachse entsprechen, so dass die Vibrationen, die von Schlägen entlang der Schlagachse herrühren, durch die Massenelemente gezielt gedämpft bzw. getilgt werden können. Dass die Massenelemente entlang genau einer Ausrichtung, beispielsweise geführt durch einen Führungsschaft beweglich sind, ermöglicht es dem Schwingungstilger, gezielt bestimmte Vibrationen und Schläge zu dämpfen. Es ist dabei auch möglich, dass verschiedene Massenelemente in verschiedenen Ausrichtungen beweglich sind. Die Massenelemente werden dabei bevorzugt bei jeglicher Bewegung aus der Ruhelage mit einer Federkraft in Richtung der Ruhelage beaufschlagt. Dies führt dazu, dass auch kleine Auslenkungen der Massenelemente eine gute Schwingungsdämpfung erzeugen können. Die Ruhelage lässt sich dabei so definieren, dass sich hier die auf das jeweilige Massenelement wirkenden Federkräfte gegenseitig aufheben.Preferably, the mass elements of the vibration absorber along exactly one orientation are movable and each have a rest position, wherein the mass elements are acted upon in a deflection from the respective rest position with a counter to the deflection spring force. The orientation in which the mass elements of the vibration absorber can move may preferably correspond to the orientation of the striking axis, so that the vibrations resulting from impacts along the striking axis can be specifically damped or eliminated by the mass elements. The fact that the mass elements are movable along exactly one orientation, for example guided by a guide shaft, enables the vibration damper to selectively dampen certain vibrations and impacts. It is there too possible that different mass elements are movable in different orientations. The mass elements are preferably applied during any movement from the rest position with a spring force in the direction of the rest position. This means that even small deflections of the mass elements can produce a good vibration damping. The rest position can be defined in such a way that here the spring forces acting on the respective mass element cancel each other out.
Besonders bevorzugt ist die Ausrichtung der Massenelemente durch je eine Führungseinrichtung definiert, wobei die Führungseinrichtungen senkrecht zu der Ausrichtung beabstandet sind. Als Führungseinrichtung kann hier beispielsweise eine Stabführung dienen, auf der jeweils eines der Massenelemente entlang der Stabrichtung gleiten kann. Es ist jedoch auch möglich, dass die Massenelemente auf andere Weise geführt werden. Die Führungseinrichtungen sind dabei bevorzugt parallel zueinander ausgerichtet und senkrecht zu dieser Ausrichtung horizontal und/oder vertikal beabstandet. Sie können somit auf jeweils einer Seite der Schlagachse innerhalb desselben Halbraums angeordnet werden, so dass eine ausgeglichene Vibrationsdämpfung auf beiden Seiten der Schlagachse eines Halbraums ermöglicht wird.Particularly preferably, the orientation of the mass elements is defined by a respective guide device, wherein the guide means are spaced perpendicular to the alignment. As guide means can serve here, for example, a rod guide on which one of the mass elements along the bar direction can slide. However, it is also possible that the mass elements are guided in other ways. The guide means are preferably aligned parallel to each other and perpendicular to this orientation horizontally and / or vertically spaced. They can thus be arranged on one side of the impact axis within the same half-space, so that a balanced vibration damping on both sides of the impact axis of a half-space is made possible.
In einer weiter bevorzugten Ausführungsform sind die Führungseinrichtungen miteinander und mit einer Beabstandungseinrichtung integral ausgeführt und insbesondere sind die Führungseinrichtungen und die Beabstandungseinrichtung als Teile eines Rahmenelements ausgeführt. Das heißt, dass die Führungseinrichtungen und die Beabstandungseinrichtung zusammen ein Bauteil bilden, das an einem Elektrowerkzeug befestigt werden kann. Durch eine derartige Ausgestaltung der Führungseinrichtungen und der Beabstandungseinrichtung ist die Montage des Schwingungstilgers an dem Elektrowerkzeug besonders einfach durchzuführen.In a further preferred embodiment, the guide means are integrally formed with each other and with a spacing device, and in particular the guide means and the spacing means are designed as parts of a frame element. That is, the guide means and the spacer means together form a component which can be attached to a power tool. By such a configuration of the guide means and the spacing means the assembly of the vibration absorber on the power tool is particularly easy to perform.
Mit Vorteil ist das Rahmenelement dabei derart ausgeführt, dass die Führungseinrichtungen im Wesentlichen zwei sich gegenüberliegende Seiten eines Rechtecks bilden und die Beabstandungseinrichtung durch zwei im Wesentlichen senkrecht zu den Führungseinrichtungen verlaufende Abstandselemente als zwei weitere sich gegenüberliegende Seiten des Rechtecks gebildet werden. Dies bedeutet, dass ein Rechteck, welches vier Seiten aufweist, durch zwei jeweils paarweise gegenüberliegende Beabstandungs- und Führungseinrichtungen gebildet wird. Demnach sind die Führungseinrichtungen sowie die Beabstandungseinrichtung im Wesentlichen parallel zueinander und bilden den rechteckigen Rahmen.Advantageously, the frame element is designed such that the guide means form substantially two opposite sides of a rectangle and the spacer means are formed by two substantially perpendicular to the guide means extending spacers as two more opposite sides of the rectangle. This means that a rectangle having four sides is formed by two pairwise opposing spacing and guiding devices. Accordingly, the guide means and the spacing means are substantially parallel to each other and form the rectangular frame.
Vorteilhafterweise bestehen die Massenelemente jeweils aus zwei Teilemementen, wobei die Teilelemente der Massenelemente insbesondere mit gegeneinander wirkenden Federkräften gegeneinander beaufschlagt sind. Da die Teilelemente gegeneinander mit Federkräften beaufschlagt sind, weisen sie eine Bewegungscharakteristik eines einzelnen Massenelements auf. Es ist daneben auch möglich, dass die Teilelemente zusammengeschraubt, gefügt oder geklebt werden, wobei eine Beaufschlagung mit Federkräften eine solche Verbindung der einzelnen Teilelemente überflüssig macht, wodurch der Zusammenbau des Schwingungstilgers erleichtert und damit begünstigt wird.Advantageously, the mass elements each consist of two Teilemementen, wherein the sub-elements of the mass elements are acted upon in particular with counteracting spring forces against each other. Since the sub-elements are acted upon against each other with spring forces, they have a movement characteristic of a single mass element. In addition, it is also possible that the sub-elements are screwed together, joined or glued, with an application of spring forces makes such a connection of the individual sub-elements superfluous, whereby the assembly of the vibration absorber is facilitated and thus favored.
Bevorzugt beträgt die Masse der schwingungsfähigen Masse des Schwingungstilgers 5% bis 10% der Masse des Elektrowerkzeugs. Eine derartige Wahl der Gesamtmasse der schwingungsfähigen Masse des Schwingungstilgers erlaubt eine effiziente Vibrationsdämpfung, ohne dass das Elektrowerkzeug durch die zusätzliche Masse unnötig schwerer gemacht wird.Preferably, the mass of the oscillatory mass of the vibration absorber is 5% to 10% of the mass of the power tool. Such a choice of the total mass of the oscillatory mass of the vibration absorber allows efficient vibration damping, without the power tool is made unnecessarily heavier by the additional mass.
Mit Vorteil beinhaltet die schwingungsfähige Masse des Schwingungstilgers Sinterstahl. Es sind jedoch andere Materialien, bevorzugt Metalle, für den Einsatz als schwingungsfähige Masse möglich.Advantageously, the oscillatory mass of the vibration damper includes sintered steel. But there are others Materials, preferably metals, for use as a vibratory mass possible.
Das erfindungsgemäße Elektrowerkzeug hat den Vorteil, dass die schwingungsfähige Masse des Schwingungstilgers besonders effizient und platzsparend ausgeführt und angeordnet ist. Das erfindungsgemäße Elektrowerkzeug ist damit für einen Benutzer wesentlich angenehmer zu bedienen, da durch den Schwingungstilger ein großer Anteil der beim Betrieb des Elektrowerkzeugs entstehenden Vibrationen gedämpft wird und das Elektrowerkzeug trotzdem gut handhabbar ist. Eine solche aktive Reduktion der Vibration, wie sie durch einen Schwingungstilger erreicht wird, kann dabei einen Anteil von mindestens 30% der gesamten Schwingungsenergie betragen.The power tool according to the invention has the advantage that the oscillatory mass of the vibration damper is designed and arranged in a particularly efficient and space-saving manner. The power tool according to the invention is thus much more comfortable to use for a user, since a large proportion of the resulting during operation of the power tool vibrations is attenuated by the vibration absorber and the power tool is still easy to handle. Such an active reduction of the vibration, as achieved by a vibration absorber, may amount to at least 30% of the total vibration energy.
Durch die bevorzugte Platzierung der schwingungsfähigen Masse des Schwingungstilgers im Bereich des Schwerpunkts des Elektrowerkzeugs wird hier eine im Vergleich zum Stand der Technik besonders effiziente Vibrationsdämpfung erreicht. Die ferner bevorzugte Ausführung der Erfindung als Einheit, nämlich als Rahmen mit darauf schwingenden schwingungsfähigen Massenelementen erleichtert zudem die Montage des Elektrowerkzeugs. Die Vibrationsdämpfung in einem erfindungsgemäßen Elektrowerkzeug kann dabei bevorzugt durch passive Einrichtungen, wie zum Beispiel gefederte Handgriffe, weiter verbessert werden.Due to the preferred placement of the oscillatory mass of the vibration absorber in the region of the center of gravity of the power tool, a particularly efficient vibration damping is achieved in comparison with the prior art. The further preferred embodiment of the invention as a unit, namely as a frame with oscillating mass elements vibrating thereon also facilitates the assembly of the power tool. The vibration damping in a power tool according to the invention can preferably be further improved by passive devices, such as spring-loaded handles.
- Fig. 1Fig. 1
- zeigt ein Elektrowerkzeug mit einem Schwingungstilger in einer Seitenansicht;shows a power tool with a vibration absorber in a side view;
- Fig. 2Fig. 2
- zeigt das Elektrowerkzeug in einer Vorderansicht;shows the power tool in a front view;
- Fig. 3Fig. 3
- zeigt einen Schwingungstilger in einer Draufsicht;shows a vibration absorber in a plan view;
- Fig. 4Fig. 4
- zeigt einen Schwingungstilger in einer Seitenansicht als Schnittdarstellung; undshows a vibration damper in a side view as a sectional view; and
- Fig. 5Fig. 5
- zeigt einen Schwingungstilger in einer perspektivischen Darstellung.shows a vibration damper in a perspective view.
Ferner umfasst das Elektrowerkzeug 10 einen Schwingungstilger 12, der zwischen dem Elektromotor 40 und dem Übertragungsgetriebe 60 angeordnet ist. Da das Übertragungsgetriebe 60, und der Elektromotor 40 jeweils in einem Getriebe- bzw. Motorgehäusen untergebracht sind, ist der Schwingungstilger 12 an dieser Position von einer Beeinflussung durch Öl, welches beispielsweise vom Übertragungsgetriebe 60 abgesondert werden kann, abgetrennt. Die Anordnung des Schwingungstilgers 12 ist dabei so gewählt, dass der Schwingungstilger 12 im Wesentlichen in einem Bereich des Schwerpunkts des Elektrowerkzeugs 10 liegt. Der Schwerpunkt des Elektrowerkzeugs 10 befindet sich unterhalb der Schlagachse Ax1 des Schlagwerks 50 und liegt im Wesentlichen auf der Drehachse Ax2 des Elektromotors 40.Furthermore, the
Der Schwingungstilger 12, der im Übrigen in den
Die Schwingung des Massenelements 14L wird dabei auch durch zwei Federelemente 16.1, 16.2 ermöglicht, welche jeweils eine Federkraft auf das Massenelement 14L ausüben. Die Federkräfte der Federelemente 16.1, 16.2 sind dabei gegeneinander gerichtet, so dass sich das Massenelement 14L ohne Einwirkung zusätzlicher äußerer Kräfte in einer Ruhelage befindet, in der die beiden Federelemente 16.1, 16.2 im Wesentlichen gleich weit komprimiert sind, so dass die Federelemente 16.1, 16.2 entgegengesetzt gleich große Kräfte auf das Massenelement 14L ausüben.The oscillation of the mass element 14L is also made possible by two spring elements 16.1, 16.2, which each exert a spring force on the mass element 14L. The spring forces of the spring elements 16.1, 16.2 are directed against each other, so that the mass element 14L is without the influence of additional external forces in a rest position in which the two spring elements 16.1, 16.2 are compressed substantially equal, so that the spring elements 16.1, 16.2 opposite equal large forces on the mass element 14L exercise.
Ferner umfasst der Schwingungstilger 12 Führungseinrichtungen 18.2, 18.4 (weitere Führungseinrichtungen 18.1, 18.3 sind in den
Die Führungseinrichtungen 18.2, 18.4 werden in der hier dargestellten Ausführungsform durch zwei Abstandselemente 22.1, 22.2 voneinander beabstandet. Die Führungseinrichtungen 18.2, 18.4 und die Abstandselemente 22.1, 22.2 bilden dabei zusammen einen in der Draufsicht erkennbaren, im Wesentlichen rechteckigen Rahmen, so dass die Massenelemente 14L, 14R entlang fester und miteinander gekoppelter Ausrichtungen A1, A2 schwingfähig sind. An den Abstandselementen 22.1, 22.2 sind darüber hinaus Befestigungsmittel in Form von Halteösen 24.1...24.4 vorgesehen, mit denen der Schwingungstilger 12 an dem Elektrowerkzeug 10 befestigt werden kann.The guide means 18.2, 18.4 are spaced apart in the embodiment shown here by two spacer elements 22.1, 22.2. The guide means 18.2, 18.4 and the spacer elements 22.1, 22.2 together form a recognizable in plan view, substantially rectangular frame, so that the mass elements 14L, 14R along fixed and mutually coupled alignments A1, A2 are capable of oscillating. On the spacer elements 22.1, 22.2 fastening means in the form of eyelets 24.1 ... 24.4 are also provided, with which the
Darüber hinaus weisen die Teilelemente 14.1, 14.2 des Massenelements 14L jeweils eine Ausnehmung auf, in die sich jeweils ein Federelement 16.1, 16.2 erstreckt. Die Federelemente 16.1, 16.2 sind daher zwischen jeweils einem Abstandselement 22.1, 22.2 und je einem Teilelement 14.1, 14.2 eingespannt und beaufschlagen die Teilelemente 14.1, 14.2 mit einer Kraft. Die Kräfte, die durch die Federelemente 16.1, 16.2 auf die Teilelemente 14.1, 14.2 ausgeübt werden, sind dabei gegeneinander gerichtet. Dies führt dazu, dass das Massenelement 14L, das aus den Teilelementen 14.1, 14.2 gebildet wird, sich in einer Ruhelage befindet, sofern die Kräfte der Federelemente 16.1, 16.2 entgegengesetzt gleich groß sind. Die Beaufschlagung mit einer Federkraft des Massenelements 14L ermöglicht es darüber hinaus, dass das Massenelement 14L bei einer von außen einwirkenden Beschleunigungskraft in Schwingung versetzt werden kann.In addition, the sub-elements 14.1, 14.2 of the mass element 14L each have a recess into which in each case a spring element 16.1, 16.2 extends. The spring elements 16.1, 16.2 are therefore clamped between in each case a spacer element 22.1, 22.2 and in each case one partial element 14.1, 14.2 and act upon the partial elements 14.1, 14.2 with a force. The forces exerted by the spring elements 16.1, 16.2 on the sub-elements 14.1, 14.2, are directed against each other. This results in that the mass element 14L, which is formed from the sub-elements 14.1, 14.2, is in a rest position, provided that the forces of the spring elements 16.1, 16.2 are opposite in size equal. In addition, the application of a spring force of the mass member 14L makes it possible to vibrate the mass member 14L at an externally applied accelerating force.
Die Dimension des Massenelements 14L und der Federelemente 16.1, 16.2 sowie die verwendeten Materialien entscheiden darüber, welche Eigenfrequenzen der Schwingungstilger 12 aufweist. Bevorzugt ist eine Eigen- oder Resonanzfrequenz des Schwingungstilgers 12 gleich einer typischen Vibrationsfrequenz, die durch das Schlagwerk 50 auf das Elektrowerkzeug 10 übertragen wird.The dimension of the mass element 14L and the spring elements 16.1, 16.2 and the materials used decide which natural frequencies the
Jeweils zwei der Führungselemente 18.1, 18.2 bzw. 18.2, 18.4 bilden dabei ein Paar, das ein Massenelement 14L, 14R in horizontaler Ausrichtung führt. Jedes der Massenelemente 14L, 14R ist dabei wie zuvor beschrieben aus jeweils zwei Teilelementen 14.1, 14.2 bzw. 14.3, 14.4 zusammengesetzt. Die Teilelemente 14.1, 14.2 bzw. 14.3, 14.4 werden wie beschrieben durch die Federelemente 16.1...16.4 zusammengehalten.In each case, two of the guide elements 18.1, 18.2 and 18.2, 18.4 form a pair that guides a mass element 14L, 14R in a horizontal orientation. Each of the mass elements 14L, 14R is composed of two subelements 14.1, 14.2 or 14.3, 14.4 as described above. The sub-elements 14.1, 14.2 and 14.3, 14.4 are held together as described by the spring elements 16.1 ... 16.4.
Dabei halten jeweils zwei der Teilelemente 14.1, 14.3 auf mittlerer Höhe der dem jeweils anderen Teilelement 14.2, 14.4 zugewandten Seitenfläche eine Einkerbung auf, die durch einen entsprechenden Vorsprung in dem jeweils anderen Teilelement 14.2, 14.4 ausgefüllt wird. Somit sind die beiden Teilelemente 14.1, 14.2 bzw. 14.3, 14.4 einerseits durch die Federelemente 16.1, 16.2 bzw. 16.3, 16.4 und andererseits durch die oben beschriebene nut- und federartige Verbindung aneinandergehalten. Weitere Befestigungsmittel der Teilelemente 14.1, 14.2 bzw. 14.3, 14.4 sind hierbei nicht vorgesehen, können jedoch zusätzlich vorhanden sein.In each case, two of the sub-elements 14.1, 14.3 hold at the middle height of the respective other sub-element 14.2, 14.4 side facing a notch, which is filled by a corresponding projection in the other sub-element 14.2, 14.4. Thus, the two sub-elements 14.1, 14.2 and 14.3, 14.4 held together on the one hand by the spring elements 16.1, 16.2 or 16.3, 16.4 and on the other hand by the nut and spring-like connection described above. Further fastening means of the sub-elements 14.1, 14.2 or 14.3, 14.4 are not provided here, but may additionally be present.
Claims (13)
dadurch gekennzeichnet, dass die Massenelemente (14L, 14R) des Schwingungstilgers (12) entlang genau einer Ausrichtung (A1, A2) beweglich sind und je eine Ruhelage aufweisen, wobei die Massenelemente (14L, 14R) bei einer Auslenkung aus der jeweiligen Ruhelage mit einer entgegen der Auslenkung wirkenden Federkraft beaufschlagt sind.Power tool (10) according to one of claims 1 to 6,
characterized in that the mass elements (14L, 14R) of the vibration absorber (12) along exactly one orientation (A1, A2) are movable and each have a rest position, wherein the mass elements (14L, 14R) at a deflection from the respective rest position with a acted upon against the deflection acting spring force.
Priority Applications (2)
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DE200850003103 DE502008003103D1 (en) | 2008-05-27 | 2008-05-27 | Power tool with vibration damper |
EP20080009603 EP2127821B1 (en) | 2008-05-27 | 2008-05-27 | Electric tool with vibration dampener |
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EP20080009603 EP2127821B1 (en) | 2008-05-27 | 2008-05-27 | Electric tool with vibration dampener |
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EP2127821A1 true EP2127821A1 (en) | 2009-12-02 |
EP2127821B1 EP2127821B1 (en) | 2011-04-06 |
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EP20080009603 Active EP2127821B1 (en) | 2008-05-27 | 2008-05-27 | Electric tool with vibration dampener |
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Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2476368A (en) * | 2009-12-16 | 2011-06-22 | Bosch Gmbh Robert | Vibration damping device for hand-held power tool |
EP2047952B1 (en) * | 2007-10-09 | 2012-08-22 | HILTI Aktiengesellschaft | Handtool machine with vibration balancing mass |
DE102011113737A1 (en) * | 2011-09-15 | 2013-03-21 | C. & E. Fein Gmbh | Oscillatory drivable machine tool e.g. grinding tool has passive damping element that is assembled at oscillation gear or motor, and is connected to actuator for active damping of vibration |
WO2015193284A1 (en) * | 2014-06-16 | 2015-12-23 | Swerea Ivf Ab | An impact machine |
US20170043466A1 (en) * | 2014-04-30 | 2017-02-16 | Hitachi Koki Co., Ltd. | Work tool |
US10232500B2 (en) | 2012-12-17 | 2019-03-19 | Swerea Ivf Ab | Impact machine |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS52109673A (en) * | 1976-03-12 | 1977-09-14 | Hitachi Koki Co Ltd | Vibration preventing apparatus in portable tools |
EP0066779A1 (en) * | 1981-06-10 | 1982-12-15 | HILTI Aktiengesellschaft | Boring or chiseling hammer |
EP1736283A2 (en) | 2005-06-23 | 2006-12-27 | Black & Decker, Inc. | Vibration dampening mechanism for a hammer drill |
EP1767315A1 (en) * | 2004-08-27 | 2007-03-28 | Makita Corporation | Working tool |
EP1779979A1 (en) * | 2004-04-30 | 2007-05-02 | Makita Corporation | Working tool |
WO2007077946A2 (en) * | 2005-12-28 | 2007-07-12 | Hitachi Koki Co., Ltd. | Impact tool |
-
2008
- 2008-05-27 DE DE200850003103 patent/DE502008003103D1/en active Active
- 2008-05-27 EP EP20080009603 patent/EP2127821B1/en active Active
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS52109673A (en) * | 1976-03-12 | 1977-09-14 | Hitachi Koki Co Ltd | Vibration preventing apparatus in portable tools |
EP0066779A1 (en) * | 1981-06-10 | 1982-12-15 | HILTI Aktiengesellschaft | Boring or chiseling hammer |
EP1779979A1 (en) * | 2004-04-30 | 2007-05-02 | Makita Corporation | Working tool |
EP1767315A1 (en) * | 2004-08-27 | 2007-03-28 | Makita Corporation | Working tool |
EP1736283A2 (en) | 2005-06-23 | 2006-12-27 | Black & Decker, Inc. | Vibration dampening mechanism for a hammer drill |
WO2007077946A2 (en) * | 2005-12-28 | 2007-07-12 | Hitachi Koki Co., Ltd. | Impact tool |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2047952B1 (en) * | 2007-10-09 | 2012-08-22 | HILTI Aktiengesellschaft | Handtool machine with vibration balancing mass |
GB2476368A (en) * | 2009-12-16 | 2011-06-22 | Bosch Gmbh Robert | Vibration damping device for hand-held power tool |
DE102011113737A1 (en) * | 2011-09-15 | 2013-03-21 | C. & E. Fein Gmbh | Oscillatory drivable machine tool e.g. grinding tool has passive damping element that is assembled at oscillation gear or motor, and is connected to actuator for active damping of vibration |
US10232500B2 (en) | 2012-12-17 | 2019-03-19 | Swerea Ivf Ab | Impact machine |
US20170043466A1 (en) * | 2014-04-30 | 2017-02-16 | Hitachi Koki Co., Ltd. | Work tool |
US10632605B2 (en) * | 2014-04-30 | 2020-04-28 | Koki Holdings Co., Ltd. | Work tool |
WO2015193284A1 (en) * | 2014-06-16 | 2015-12-23 | Swerea Ivf Ab | An impact machine |
US10549414B2 (en) | 2014-06-16 | 2020-02-04 | Swerea Ivf Ab | Impact machine |
Also Published As
Publication number | Publication date |
---|---|
DE502008003103D1 (en) | 2011-05-19 |
EP2127821B1 (en) | 2011-04-06 |
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