EP2480382B1 - Outil électrique avec compensateur de vibrations destiné à compenser les vibrations du boîtier de l'outil électrique - Google Patents

Outil électrique avec compensateur de vibrations destiné à compenser les vibrations du boîtier de l'outil électrique Download PDF

Info

Publication number
EP2480382B1
EP2480382B1 EP10739561.8A EP10739561A EP2480382B1 EP 2480382 B1 EP2480382 B1 EP 2480382B1 EP 10739561 A EP10739561 A EP 10739561A EP 2480382 B1 EP2480382 B1 EP 2480382B1
Authority
EP
European Patent Office
Prior art keywords
power tool
balancing mass
movement
drive
driving
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP10739561.8A
Other languages
German (de)
English (en)
Other versions
EP2480382A1 (fr
Inventor
Willy Braun
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2480382A1 publication Critical patent/EP2480382A1/fr
Application granted granted Critical
Publication of EP2480382B1 publication Critical patent/EP2480382B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • B25D2217/0088—Arrangements for damping of the reaction force by use of counterweights being mechanically-driven

Definitions

  • the present invention relates to a power tool according to the preamble of patent claim 1 with a counteroscillator, which is provided to compensate for housing vibrations of the power tool, which includes a striking mechanism, in this, and which comprises a drive means and a balancing mass.
  • Such a power tool is for example from the DE 10 2006 053 105 A1 .
  • the subject of vibration is becoming more and more important for power tools, especially for drills and impact hammers.
  • FIG. 12 shows a typical housing vibration 100 resulting from vibrations of the housing of drill and percussion hammers 7 caused by a striking mechanism assembly 8 in which the beater 81 is driven by an eccentric piston drive 12 becomes.
  • the rotation angle [in °] is shown, on the vertical axis 102, the deflection [in mm] of the housing.
  • the vibration generating case vibration 100 is composed of a plurality of frequency components. The main frequency is derived from the periodic acceleration of the racket 81.
  • a damper is a spring-mass system with a fixed resonant frequency that can achieve significant vibration reduction only in a small region near the resonant frequency.
  • a balancing mass is coupled to the drive of the electric tool and is driven in such a way that the reaction force resulting from the drive of the counteroscillator works as well as possible against the vibration source.
  • balancing mass of a counter-oscillator can be divided into two classes: In the first case, the balancing mass is forcibly driven by means of an eccentric crank or cross-grinding drive.
  • the balancing mass is driven by cams, wherein the required contact contact is made by means of a spring loading of the balancing mass. In this case, the balancing mass is not forced.
  • Examples of a force-driven balancing mass show the publications EP 1 475 190 A2 and EP 1 439 038 A1 .
  • the balancing mass is arranged around the hammer tube and is driven by an additional connecting rod linked to the striking mechanism eccentric.
  • the EP 1 439 038 A1 is a cuboid, provided with a transverse slot balancing mass disposed above the eccentric. In the transverse slot runs to the axis of rotation eccentric bolt of Schlagtechniksexzenters so that the balancing mass is driven by a cross-loop.
  • the previously known embodiments have in common that they only attenuate caused by the periodic acceleration of the racket housing vibration. Frequency components from other sources of vibration can not be compensated with the previously known embodiments.
  • the object of the invention is therefore to provide a power tool with a counteroscillator, with which the housing vibration of the power tool can be better reduced can.
  • a power tool according to claim 1 with a counteroscillator, which is provided to compensate for housing vibrations of the power tool, which includes a percussion unit, in this, wherein the counteroscillator comprises a drive means and a balancing mass, wherein the drive means with the balancing mass so is coupled, that by driving the drive means about a drive axis a harmonic rotational movement of the drive means in an inharmonic thrust movement of the balancing mass is convertible.
  • a harmonic rotary motion within the meaning of the invention is a rotary movement with a constant fundamental frequency.
  • the change of location with time has an unifrequent sinusoidal course.
  • the change of location with time has a multifrequency course.
  • the counteroscillator therefore converts a uniform rotational movement into a pushing movement with a course of motion which can be broken down by Fourier analysis into a sinusoidal oscillation with basic frequency and at least one harmonic.
  • the balancing mass according to the invention performs an inharmonic pushing movement, with such a counteroscillator not only a vibration caused by a unifrequent cyclic movement of a component, in particular a racket of a striking mechanism, can be compensated.
  • vibrations of other vibration sources which are caused for example by impact or recoil a beating chain, by game between components, by non-linear elasticity, by only approximately harmonic reaction forces of the percussion or unbalanced mass forces of the drive are due to the superposition of vibrations of other frequency components for Oscillation with fundamental frequency compensated.
  • the balancing mass is positively driven by the drive means.
  • the transmission of motion between the drive means and the balancing mass is clear even at high reaction forces and high operating frequency.
  • no additional pressure means such as springs are needed, so that the effort, space and cost is reduced compared to non-positively driven embodiments of counter-oscillators.
  • no energy required for the pressing force or due to friction and additional wear effects, must be provided by the engine power.
  • the balancing mass is positively and / or non-positively coupled to the drive means.
  • a counteroscillator is therefore feasible by a variety of embodiments. In particular, the number of transmission components of the counter-oscillator is variable.
  • the balancing mass can be moved back and forth in a direction of movement essentially from a starting point and returns to the starting point.
  • the balancing mass is therefore cyclically reciprocated by the drive means.
  • counter-oscillators can be used, in which the drive means for driving the balancing mass cyclically performs a complete revolution about the drive axis, and in which the drive means for driving the balancing mass cyclically performs a partial rotation about the drive axis.
  • a drive cycle of the drive means may therefore both a complete revolution of the drive means about the drive axis depending on the choice of the counter-oscillator as well as a partial revolution of the drive means about the drive axle.
  • the drive means has a means for coupling and the balancing mass an antidote for coupling. In order to ensure a safe transmission of motion, the means for coupling cooperates with the means for negative feedback.
  • the means for coupling is a receiving means and the counter-means for coupling a guide means, or the means for coupling is a guide means and the counter-means for coupling is a receiving means.
  • the guide means cooperating with the receiving means the transmission of movement between the drive means and the balancing mass is ensured.
  • the receiving means and / or the guide means has a contour, wherein by rotation of the drive means, the guide means along the receiving means, or the receiving means along the guide means is movable. Since the guide means along the receiving means or the receiving means along the guide means is movable, the amount and the direction of deflection of the compensating cup is substantially determined by the contour.
  • the contour and its pitch both a multiple back and forth oscillating balance mass and one or more rest points of the balancing mass can be achieved within a drive cycle of the drive means.
  • the contour therefore makes it possible to accelerate the movement of the balancing mass and to perform shock processes with the balancing mass.
  • the contour allows a temporal extension of forward and backward movements of the balancing mass. Therefore, both phase-shifted vibration processes as well as acceleration and shock processes, such as the striking mechanism, can be very well balanced.
  • the coupling means has an eccentricity to the drive axle. Due to the eccentricity of the amount of maximum deflection of the balancing mass is at least partially transverse to the drive axis Movement direction can be enlarged.
  • the direction of movement, in which the compensating mass is moved back and forth by driving the drive means substantially transversely to the drive axis, or it runs substantially parallel to the drive axis.
  • the receiving means is preferably designed as a groove, indentation, web or recess.
  • the guide means is designed as a cam, pin, bolt, bulge or web.
  • the guide means and / or the receiving means is preferably provided with a rotating means, for example a sleeve, a wheel or a rotatable bearing.
  • a cam acts as a guide means with a recess as a receiving means, wherein the cam is arranged in the recess.
  • a pin cooperates as a guide means with a groove as a receiving means, wherein the pin engages in the groove.
  • a web acts as a guide means with a groove as a receiving means, wherein the web engages in the groove.
  • a cam acts as a guide means with a groove as a receiving means, wherein the groove engages around the cam.
  • a nearly arbitrary course of movement of the balancing mass can be achieved by adjusting the contour of the cam, the web or the groove.
  • the amount of deflection of the balancing mass is determined by the respective contour, and optionally by the eccentricity of the means for coupling to the drive axis at least partially transverse to the drive axis extending direction of movement.
  • the balancing mass is forcibly driven by the drive means and a defined movement ensured.
  • the drive means has at least two driving bolts as guide means, and the compensating mass as receiving means has at least two driving webs.
  • the driving bolts take the driving webs alternately with the rotation of the drive means, so that the balancing mass is moved back and forth.
  • the driving pins and the driving webs act like a step gear together. The deflection of the balancing mass is determined by the position of the driving pin on the cam and the length and contour of the webs.
  • the driving bolts are arranged on a cam of the drive means, which engages in a recess of the balancing mass, so that the cam acts as a guide means and the recess as an engagement means.
  • the deflection of the balancing mass is additionally determined by the contour of the cam, and by the eccentricity of the cam at least partially transverse to the drive axis extending direction of movement. This embodiment also makes it possible to accelerate or slow down the movement of the balancing mass.
  • the drive means comprises a multi-joint transmission and the balancing mass is arranged on a transmission component of the multi-joint transmission.
  • the direction of movement of the balancing mass and its speed by the number of gear parts and their arrangement are determined to each other.
  • the mentioned embodiments can be combined with one another in order to change the course of movement of the balancing mass, in particular the time or the amount of deflection of the balancing mass, or its direction of movement.
  • the direction of movement of the balancing mass can be changed by additional transmission components.
  • additional driving bolts and driving webs resting breaks the movement of the balancing mass can be realized.
  • the power tool according to the invention has the advantage that due to the inharmonic pushing movement of the balancing mass of the counter-oscillator housing vibrations of the power tool are better damped.
  • An electric power tool according to the invention with a hammer mechanism is, for example, a hammer drill or a hammer, but also a power tool without a hammer mechanism, for example a jigsaw.
  • the power tool comprises an eccentric disc, on which in particular a connecting rod for driving the percussion mechanism assembly is arranged, wherein the eccentric disc is rotatably mounted about an eccentric axis, wherein the drive axis of the drive means is the eccentric axis of the power tool.
  • the drive means is mounted centrally or eccentrically rotatable about the eccentric axis. Due to the eccentric arrangement of the drive means about the eccentric axis, the amount of deflection of the balancing mass can be increased.
  • the eccentric disc is the drive means, so that no additional components for the drive means are needed and the counteroscillator is very space-saving and inexpensive in the power tool can be integrated.
  • An embodiment is furthermore preferred in which the motor axis of the drive motor forms the drive axle.
  • the motor shaft extending in the direction of the motor axis preferably drives a non-circular gear, which drives both the striking mechanism assembly and the balancing mass.
  • Fig. 1 shows, as already described in the introductory part of this patent application, a typical housing vibration, which results from vibrations of the housing of drilling and hammering.
  • Fig. 2-4 each show a section of a power tool 7 with striking mechanism assembly 8, wherein the power tool 7 is here a hammer drill, and wherein in Fig. 2 a longitudinal section through the power tool 7 is shown in FIG Fig. 3 a plan view of an eccentric 10 of the power tool 7, and Fig. 4 a horizontal section through a balancing mass 2 of a arranged in the power tool 7 Gegenschwingers. 1
  • the electric tool 7 is driven by means of an electric motor (not shown here), wherein the electric motor 7 drives a motor shaft 9 with a drive pinion 91, and wherein the drive pinion 91 drives the eccentric disk 10.
  • the eccentric 10 is rotatably mounted on an eccentric shaft 32 which is rotatably supported by a first eccentric 61 and a second eccentric 62 about an eccentric axis 33.
  • the first eccentric bearing 61 is arranged in a housing 14 of the striking mechanism assembly 8 and the second eccentric bearing 62 in the bearing block 13, wherein the bearing block 13 itself is also arranged in the housing 14 of the striking mechanism assembly 8.
  • a spur gear 17 is further arranged rotatably, which drives a clutch spur gear 16 and a bevel gear 15.
  • the bevel gear 15 drives a driven gear 18, which is arranged around a hammer tube 19 of the striking mechanism assembly 8, so that it is driven.
  • a connecting rod 12 is eccentrically arranged eccentrically about the eccentric axis 33 by means of an eccentric pin 11.
  • the connecting rod 12 drives a racket 81 of the striking mechanism assembly 8 cyclically in a substantially harmonic pushing movement.
  • the counteroscillator 1 has a drive means 3 and a balancing mass 2.
  • the drive means 3 is rotatably mounted about a drive axis 33 and converts a rotational movement of the drive means 3 about the drive axis 33 into a pushing movement of the balancing mass 2.
  • the counteroscillator 1 is arranged between the eccentric disk 10 and the bearing block 13.
  • the drive means 3 is coupled to a means for coupling 31 by means of a negative feedback 21 with the balancing mass 2 in order to ensure a secure transmission of movement.
  • the means for coupling 31 is here as a guide means, namely as a cam 31 is formed.
  • the cam is non-rotatably disposed about the drive shaft 32, which is here the eccentric shaft, so that the eccentric axis 33 is a drive axle 33 of the drive means 3.
  • cams and means for coupling 31 are used synonymously.
  • the antidote to the coupling 21, with which the cam 31 cooperates receiving means, namely a recess 21 of the balancing mass 2.
  • recess is therefore used synonymously with the antidote for coupling 21st
  • the cam 31 engages in the recess 21 of the balancing mass 2.
  • the drive means 3 and the balancing mass 2 are thereby coupled so that the balancing mass 2 is forcibly driven by the latter when rotating the drive means 3.
  • the cam 31 of the counter-oscillator 1 has a circular contour 35.
  • the cam 31 rotates eccentrically on rotation of the drive means 3 about the drive axis 33.
  • Die Fig. 4 shows the eccentricity 331 of the cam 31 at a partial revolution of the drive means 3 about the drive axis 33.
  • the recess 21 and the cam 31 are dimensioned such that when rotating the cam 31 in a rotational direction 4 is always a contact contact between the cam 31 and the recess 21st consists.
  • the cam 31 rotates eccentrically about the drive axis 33 in the direction of rotation 4, it therefore displaces the balancing mass 2 axially.
  • the leveling compound 2 is thus moved back and forth in a direction of movement 5, which extends here transversely to the drive axis 33.
  • the balancing mass 2 in the power tool 7 in the direction of movement 5 can move freely back and forth, recesses 22 are provided on her.
  • Fig. 16 a shows the course of the movement 100 of the balancing mass 2 in a 360 ° rotation of the drive means 3 about the drive axis 33.
  • the deflection [in mm] of the balancing weight 2 On the horizontal axis 101 of the rotation angle [in °], on the vertical axis 102, the deflection [in mm] of the balancing weight 2.
  • the amplitude of the course of the vibration 100 of the balancing mass 2 corresponds to the eccentricity 331.
  • the counteroscillator 1 is indeed provided so that there is a phase shift to the harmonic oscillatory movement of the racquet 81 percussion unit 8, however, can be effected with this counteroscillator 1, only a harmonic countermovement.
  • a motion compensation that takes into account inharmonic parts is not possible. Therefore, no damping of a housing oscillation can be achieved with this counteroscillator 1, which is caused in addition to the periodic acceleration of the racket 81 by still further sources of vibration
  • Fig. 5 - 11 show counteroscillator 1 different embodiments of the invention.
  • the counter-oscillators 1 listed here are inharmonic pushing movements of the balancing mass 2 executable, so that these counteroscillator 1, a damping of the housing oscillation, which is caused by further sources of vibration, allow.
  • Fig. 5 is arranged eccentrically on the drive means 3 as means for coupling 31 a pin.
  • the balancing mass 2 has, as an antidote to the coupling 21, a symmetrical groove into which the pin 31 engages.
  • the means for coupling 31 is therefore provided here as a guide means and the means for negative feedback 21 as receiving means.
  • pen and means for coupling 31, as well as the terms groove and means for negative feedback 21 are each used synonymously.
  • the groove 21 has a symmetrical V-shaped contour 25 with an angle of attack 251.
  • the groove 21 is not circular but V-shaped, and therefore the pin 31 can not move freely along the groove 21, the pin 31 presses in its eccentric movement about the drive shaft 33 against the balancing mass 2 and moves it axially.
  • the Fig. 5 a) shows the balancing mass 2 at a starting point 20 at a rotational angle of 0 ° of the drive means 3.
  • the Fig. 5b) shows the balancing mass 2 after a partial revolution of the drive means 3, through which the balancing mass 2 has moved axially relative to the starting point 20 by a deflection amount 201 in a direction of movement 5.
  • Fig. 16c shows the course of the movement 100 of the balancing mass 2 of the counter-oscillator 1 of Fig. 5 in the case of a 360 ° revolution of the drive means 3 about the drive axis 33. Again, the rotation angle [in °] on the horizontal axis 101 and the deflection [in mm] of the compensation mass 2 on the vertical axis 102 are shown.
  • the counter-oscillator 1 can be changed over the angle of attack 251 of the groove 21 and the eccentricity 331 of the pin 31, the movement.
  • the counteroscillator 1 allows, as in Fig. 16c) represented opposite the counteroscillator of Fig. 2-4 steeper movement or acceleration amplitudes and resting phases.
  • this balancing mass has 2 recesses 22.
  • drive means 3 for example, the eccentric 10 of a power tool 7, wherein the pin 31 is arranged eccentrically on the eccentric disk 10 is suitable.
  • Fig. 6 is another counteroscillator 1 shown.
  • Fig. 6 a) shows a plan view of the counteroscillator while Fig. 6b) a section through the line A --- A shows.
  • On the drive means 3 a first driving pin 311 and a second driving pin 312 are arranged as means for coupling 31.
  • the balancing mass 2 has, as a means for negative feedback 21, a first driving rib 211 and a second moving rib 212, which protrude into a recess 24 of the balancing mass 2 here.
  • the recess 24 itself is here dimensioned so that it does not affect the movement of the balancing mass 2.
  • the first driving pin 311 is arranged so that when turning the drive means 3 in the direction of rotation 4 in touching contact with the first driving bar 211 and the balance mass 2 entrains and axially displaces in the direction of movement 5 until it comes out of touch contact with the first driving bar 211 ,
  • the second driving pin 312 is arranged so that it is in contact with the second when rotating the drive means 3 in the direction of rotation 4
  • Mit Erasmusesteg 212 device and the balancing mass 2 entrains and shifts axially in the opposite direction of movement 5 until it comes out of touch contact with the second driving bar 212.
  • the driving webs 211, 212 and driving pins 311, 312 are also arranged so that they come into contact contact and out of touch successively. In a 360 ° rotation of the drive means 3, therefore, the leveling compound 2 is once again moved back and forth.
  • the counter-oscillator 1 can be about the number and position of the driving pins 311, 312 and driving webs 211, 212 and the contour 25 of the driving webs 211, 212 change the movement.
  • the backswing of the Fig. 7 has analogous to the counteroscillator of Fig. 2-4 as a means for coupling 31, a guide means, namely a cam 31 which is rotatably mounted on the drive shaft 32 and rotatable about the drive shaft 33.
  • cam and means for coupling 31 are used synonymously.
  • the antidote to the coupling 21, with which the cam 31 cooperates is also a receiving means a recess 21 of the balancing mass 2, so that here too the term recess is used synonymously for the antidote to the coupling 21.
  • the cam 31 engages in the recess 21 of the balancing mass 2, so that the drive means 3 and the balancing mass 2 are coupled so that the balancing mass 2 is forcibly driven during rotation of the drive means 3 and axially moved back and forth.
  • a curvy contour 35 namely the contour 35 of a Gleichdicks.
  • FIG. 7 a Analogous to Fig. 5 show the Fig. 7 a) the balancing mass 2 at a starting point 20 at a rotation angle of 0 ° of the drive means 3.
  • Die Fig. 7b) shows the balancing mass 2 after a partial revolution of the drive means 3, through which the balancing mass 2 has moved axially relative to the starting point 20 by a deflection amount 201 in a direction of movement 5.
  • Fig. 7 a harmonic rotation of the drive means 3 leads to an inharmonic pushing movement of the balancing mass 2.
  • the course of the vibration 100 of the balancing mass 2 with time is multifrequent.
  • Fig. 16b shows the course of the movement 100 of the balancing mass 2 in a 360 ° rotation of the drive means 3 about the drive axis 33.
  • the cam 31 is preferably arranged on the eccentric shaft 32 of the power tool 7.
  • Fig. 8 shows a counteroscillator 1, the drive means 3 as a means for coupling 31 has a groove with a curved contour 35.
  • the groove is therefore here a receiving means, in which engages a pin of the balancing mass 2 as a guide means.
  • the terms groove and means for coupling 31 and the terms pin and means for negative feedback 21 are therefore for the Fig. 8 used synonymously.
  • Fig. 8b) is compared to Fig. 8 a) an additional gear member 23 is provided, with which the balancing mass 2 is spatially offset relative to the drive means 3.
  • the additional transmission component 23 is mounted, for example, on the housing 14 of the power tool 7 by means of a bearing 6.
  • the distance of the contour 35 of the groove 31 of the drive means of the counter-oscillator 1 of Fig. 8 varies to the drive axis 33. Therefore, in this embodiment of the counteroscillator 1, an almost arbitrary course of motion 100 of the balancing mass 2 can be generated.
  • the Fig. 16d) shows by way of example a profile of the movement 100 of the balancing mass 2 of such a counter-oscillator 1.
  • the groove 31 is preferably arranged in the eccentric disk 10 of the power tool 7, for example milled.
  • this counteroscillator 1 can be integrated very cost-effectively in the power tool 7 in a very space-saving manner and with minimal component expenditure.
  • the pin 21 may for example be provided with a sleeve or a rotatable bearing.
  • FIGS. 9 and 10 schematically show further embodiments of counter-oscillators 1.
  • the contour 35 of the drive means 3 is also curved.
  • the coupling means 31 is in each case a guide means, namely in the Fig. 9 a jetty and in the Fig. 10 a cam.
  • the antidote to the coupling 21 is provided in both cases as a receiving means, namely as a groove, in each case sleeves or rotatable bearings allow a low-friction interaction of the guide means with the receiving means.
  • the balancing mass 2 is offset in both counter-oscillators 1 by additional transmission components 231, 232 relative to the drive means 3, wherein the transmission components 231, 232 may be mounted for example on the housing 14 of the power tool 7 by means of bearings 6.
  • the Fig. 11 shows analogous to Fig. 7 a counteroscillator 1, wherein the drive means 3 has a cam as a means for coupling 31, wherein the balancing mass 2 has a recess as a means for negative feedback 21, in which engages the cam.
  • the terms cam and means for coupling 31 and the terms recess and means for negative feedback 21 are therefore for the Fig. 11 used synonymously.
  • the cam 31 of the counter-oscillator 1 of Fig. 11 a curved contour 35, and further, the recess 21 has a profile of the movement 100 of the balancing mass 2 influencing contour 25. Even with this counteroscillator 1, therefore, almost any course of motion 100 of the balancing mass 2 can be made possible. Within a 360 ° rotation of the drive means 3 in the direction of rotation 4 about the drive axis 33, therefore, both returning motions and waveforms having a plurality of frequency components can be realized.
  • a multi-joint transmission as a counteroscillator 1.
  • the multi-joint transmission has a first connection component 36 and a second connection component 37, which are each connected to one another at a connection point 39 by means of a connecting rod 38.
  • the first connection component 36 is rotatably mounted, for example, on the housing 14 of the power tool 7.
  • the second connecting member 37 is rotatably supported about the drive shaft 33. When rotating the second connecting member 37 in the direction of rotation 4 about the drive shaft 33 arranged on the connecting rod 38 balancing mass 2 is deflected and moved back and forth.
  • Fig. 12 is the deflection of the balancing mass 2 relative to a reference position 104 as an arrow 107, and its course 106 shown within a 360 ° - rotation of the drive means 3 about the drive axis 33.
  • Fig. 17 shows the deflection of the balancing mass 105 as a function of time.
  • the amount of deflection [in mm] is plotted on the vertical axis 102 and the time [in s] on the horizontal axis 103.
  • the Fig. 17 shows that also with the counteroscillator 1 of the Fig. 12 an inharmonic pushing movement of the balancing mass 2 can be achieved.
  • the course of movement of the balancing mass 2 can be adjusted by the number, shape and arrangement of the transmission components 36-39.
  • Fig. 13 - 15 schematically show further embodiments which do not fall under the scope of the claims, with counter-oscillators 1.
  • the drive means 3 is rotatably mounted about a drive axis 33 and has as means for coupling 31 a receiving means, namely a groove.
  • the balancing mass 2 has, as a means for negative feedback 21 in each case a guide means, namely a pin which engages in the groove. Therefore, the terms groove and means for coupling 31 and the terms pen and means for negative feedback 21 are used synonymously below.
  • the direction of movement 5 of the leveling compound 2 extends in all three cases essentially parallel to the drive axis 33.
  • the groove 31 has a curved contour 35.
  • a counteroscillator 1 can cyclically cause a movement of the leveling compound 2, which contains back and forth movements as well as accelerations and decelerations.
  • the counteroscillator 1 can be adapted in particular by changing the contour 25, 35, eccentricity 331 and / or arrangement of additional transmission components with simple means to the vibration conditions of power tools 7. They therefore enable optimal vibration reduction.

Landscapes

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

Claims (12)

  1. Outil électrique (7) présentant un module de percussion (8) et un disque excentrique (10) sur lequel est disposée une manivelle (12) qui entraîne un percuteur (81) du module de percussion (8),
    le disque excentrique (10) étant monté à rotation autour d'un axe excentrique (33),
    l'outil électrique présentant un contre-oscillateur (1) prévu pour compenser les vibrations du boîtier à l'intérieur de l'outil électrique (7), et comportant un moyen d'entraînement (3) et une masse d'équilibrage (2),
    le moyen d'entraînement (3) étant prévu de manière à pouvoir tourner autour d'un axe d'entraînement (33) formé par l'axe excentrique (33),
    le moyen d'entraînement (3) présentant un moyen d'accouplement (31) et la masse d'équilibrage (2) un moyen complémentaire d'accouplement (21) qui coopère de telle sorte que la masse d'équilibrage (2) se déplace axialement d'une certaine distance (201) dans une direction de déplacement (5) par la rotation du moyen d'entraînement (3) autour de l'axe d'entraînement (33), caractérisé en ce que
    le moyen d'accouplement (31) est configuré comme moyen de reprise (21, 31) et le moyen complémentaire d'accouplement (21) comme moyen de guidage (21, 31) ou inversement,
    en ce que le moyen de guidage (21, 31) s'engage dans le moyen de réception (21, 31) et
    en ce que le moyen de réception (21, 31) et/ou le moyen de guidage (21, 31) présente un contour (35) dont la pente se modifie de telle sorte que le niveau de déviation (201) duquel la masse d'équilibrage (2) est déplacée dans la direction de déplacement (5) par la rotation du moyen d'entraînement (3) se modifie de manière non harmonique et que par entraînement du moyen d'entraînement (3), un déplacement de rotation harmonique du moyen d'entraînement (3) soit converti en un déplacement non harmonique de poussée de la masse d'équilibrage (2).
  2. Outil électrique (7) selon la revendication 1, caractérisé en ce que la masse d'équilibrage (2) est entraînée de manière forcée par le moyen d'entraînement (3).
  3. Outil électrique (7) selon l'une des revendications précédentes, caractérisé en ce que par rotation du moyen d'entraînement (3) autour de l'axe d'entraînement (33), la masse d'équilibrage (2) est déplacée dans une direction de déplacement en va-et-vient essentiellement dans une direction de déplacement (5), partant d'un point de départ (20) pour revenir ensuite vers le point de départ (20).
  4. Outil électrique (7) selon l'une des revendications précédentes, caractérisé en ce que le contour (35) a la forme d'un V ou une forme incurvée.
  5. Outil électrique (7) selon l'une des revendications précédentes, caractérisé en ce que par la rotation du moyen d'entraînement (3), le moyen de guidage (21, 31) peut être déplacé le long du moyen de réception (21, 31) ou le moyen de réception (21, 31) peut être déplacé le long du moyen de guidage (21, 31).
  6. Outil électrique (7) selon l'une des revendications précédentes, caractérisé en ce que le moyen d'accouplement (31) présente une excentricité (331) par rapport à l'axe d'entraînement.
  7. Outil électrique (7) selon l'une des revendications précédentes, caractérisé en ce que le moyen de réception (21, 31) est configuré comme rainure, creux ou découpe.
  8. Outil électrique (7) selon l'une des revendications précédentes, caractérisé en ce que le moyen de guidage (21, 31) est configuré comme cane, tige, saillie ou nervure.
  9. Outil électrique (7) selon l'une des revendications précédentes, caractérisé en ce qu'une cane servant de moyen de guidage (21, 31) coopère avec une découpe servant de moyen de réception (21, 31), la cane d'engageant dans la découpe.
  10. Outil électrique (7) selon la revendication 9, caractérisé en ce qu'au moins deux goujons d'entraînement (311, 312) sont disposés sur le moyen d'entraînement (3) et au moins deux traverses d'entraînement (231, 232) sont disposées sur la masse d'équilibrage (2).
  11. Outil électrique (7) selon l'une des revendications 1 à 10, caractérisé en ce que le moyen d'entraînement (3) est monté à rotation centrée ou décentrée autour de l'axe excentrique (33).
  12. Outil électrique (7) selon l'une des revendications 1 à 11, caractérisé en ce que le disque excentrique (10) forme le moyen d'entraînement (3).
EP10739561.8A 2009-09-24 2010-07-27 Outil électrique avec compensateur de vibrations destiné à compenser les vibrations du boîtier de l'outil électrique Not-in-force EP2480382B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910044941 DE102009044941A1 (de) 2009-09-24 2009-09-24 Gegenschwinger, der zum Ausgleich von Gehäusevibrationen eines Elektrowerkzeugs in diesem vorsehbar ist
PCT/EP2010/060855 WO2011035956A1 (fr) 2009-09-24 2010-07-27 Compensateur de vibrations destiné à compenser les vibrations du boîtier d'un outil électrique

Publications (2)

Publication Number Publication Date
EP2480382A1 EP2480382A1 (fr) 2012-08-01
EP2480382B1 true EP2480382B1 (fr) 2017-07-19

Family

ID=42739224

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10739561.8A Not-in-force EP2480382B1 (fr) 2009-09-24 2010-07-27 Outil électrique avec compensateur de vibrations destiné à compenser les vibrations du boîtier de l'outil électrique

Country Status (3)

Country Link
EP (1) EP2480382B1 (fr)
DE (1) DE102009044941A1 (fr)
WO (1) WO2011035956A1 (fr)

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB223350A (en) * 1923-08-11 1924-10-23 Henry Snowden Rowell Improvements in or relating to the balancing of reciprocating engines
GB1086430A (en) * 1966-09-20 1967-10-11 Miles Eng Ltd F G An actuator mechanism
DE19804653C2 (de) * 1998-02-06 2001-03-08 Rheinmetall W & M Gmbh Großkalibrige Waffe
JP4195818B2 (ja) 2003-01-16 2008-12-17 株式会社マキタ 電動ハンマ
EP1779980A3 (fr) 2003-03-21 2014-01-08 Black & Decker, Inc. Système limitant les vibrations pour outil électrique, et outil électrique incorporant ce système
DE602004026243D1 (de) 2003-05-09 2010-05-12 Makita Corp Elektrowerkzeug
EP1491277B1 (fr) * 2003-06-23 2006-01-18 Makita Corporation Outil motorisé animé d'un mouvement alternatif
JP2008068385A (ja) * 2006-09-15 2008-03-27 Hitachi Koki Co Ltd 電動工具
DE102006053105A1 (de) * 2006-11-10 2008-05-15 Robert Bosch Gmbh Handwerkzeugmaschinenschlagwerkvorrichtung
US8549762B2 (en) * 2007-02-13 2013-10-08 Robert Bosch Gmbh Linkage drive mechanism for a reciprocating tool
DE102008000677A1 (de) * 2008-03-14 2009-09-17 Robert Bosch Gmbh Handwerkzeugmaschine für schlagend angetriebene Einsatzwerkzeuge

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP2480382A1 (fr) 2012-08-01
DE102009044941A1 (de) 2011-03-31
WO2011035956A1 (fr) 2011-03-31

Similar Documents

Publication Publication Date Title
EP1725373B9 (fr) Transmission a came oscillante
EP2234768B1 (fr) Entraînement oscillant d'une machine-outil à main
DE19851888C1 (de) Bohrhammer
DE102009047106A1 (de) Variation der Eigenfrequenz von Schwingungsmitteln in Elektrowerkzeugen
EP3227056B1 (fr) Machine-outil à main
DE112012005769T5 (de) Schlagwerkzeug
EP2480381B1 (fr) Entraînement à bielle avec élément oscillant supplémentaire
DE102006059076A1 (de) Schlagwerk einer Elektrohandwerkzeugmaschine
EP2250308B1 (fr) Dispositif d'aiguilletage d'une bande fibreuse
EP0973974B1 (fr) Outil, notamment pilonneuse pour compacter le sol ou marteau
DE102006032214A1 (de) Handwerkzeugmaschine mit einer Schlagwerkeinheit
EP2480382B1 (fr) Outil électrique avec compensateur de vibrations destiné à compenser les vibrations du boîtier de l'outil électrique
EP1677950B1 (fr) Outil de percussion pour une machine-outil a main
EP2504603A1 (fr) Amortisseur de vibration commandé
WO2011160147A2 (fr) Dispositif de forge
WO2011035955A1 (fr) Outil électrique comprenant un ensemble de percussion et une masse d'équilibrage pour la compensation des vibrations de l'outil électrique
EP2448719A1 (fr) Dispositif de réduction et/ou compensation de vibrations, en particulier pour une machine-outil à main, destiné à être utilisé dans des machines-outils à main
EP2104596A1 (fr) Mécanisme de percussion d'une machine-outil électrique portative
EP4324597A1 (fr) Marteau perforateur ou burineur avec une unité de percussion à vibrations réduites
DE102005001339A1 (de) Kraftgetriebenes Schlagwerkzeug
WO2012045504A1 (fr) Amortisseur de vibrations multidimensionnel
WO2011064027A1 (fr) Outil électrique avec réducteur de vibration adaptatif
EP1527826A1 (fr) Générateur de vibration et dispositif pour examiner la résistance à la flexion
DE102007062545A1 (de) Schlagwerkeinheit

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20120424

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20170330

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 909932

Country of ref document: AT

Kind code of ref document: T

Effective date: 20170815

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502010013885

Country of ref document: DE

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20170830

Year of fee payment: 8

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20170719

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170719

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171019

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170719

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170719

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170719

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170719

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171019

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171020

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170719

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170719

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20171119

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170719

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502010013885

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170719

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170719

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170731

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170719

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170719

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170731

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170727

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20170731

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170719

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170719

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170719

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170719

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20180524

26N No opposition filed

Effective date: 20180420

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170727

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170731

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170719

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170919

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 909932

Country of ref document: AT

Kind code of ref document: T

Effective date: 20170727

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170719

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170727

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20180727

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180727

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20100727

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170719

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20190924

Year of fee payment: 10

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170719

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170719

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170719

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170719

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502010013885

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210202