CN102510791B - Power tool comprising a percussion assembly and a counterweight for compensating vibrations of the power tool - Google Patents
Power tool comprising a percussion assembly and a counterweight for compensating vibrations of the power tool Download PDFInfo
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- CN102510791B CN102510791B CN201080042521.3A CN201080042521A CN102510791B CN 102510791 B CN102510791 B CN 102510791B CN 201080042521 A CN201080042521 A CN 201080042521A CN 102510791 B CN102510791 B CN 102510791B
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- balance mass
- electric tool
- drive unit
- coupling device
- vibration
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- 238000009527 percussion Methods 0.000 title abstract 4
- 230000008878 coupling Effects 0.000 claims description 45
- 238000010168 coupling process Methods 0.000 claims description 45
- 238000005859 coupling reaction Methods 0.000 claims description 45
- 230000007246 mechanism Effects 0.000 claims description 42
- 238000006243 chemical reaction Methods 0.000 claims description 14
- 230000013011 mating Effects 0.000 claims description 12
- 230000033001 locomotion Effects 0.000 description 60
- 230000008859 change Effects 0.000 description 27
- 238000000034 method Methods 0.000 description 14
- 230000008569 process Effects 0.000 description 14
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- 230000001133 acceleration Effects 0.000 description 6
- 230000006978 adaptation Effects 0.000 description 4
- 238000009826 distribution Methods 0.000 description 4
- 238000004062 sedimentation Methods 0.000 description 4
- 230000005540 biological transmission Effects 0.000 description 3
- 230000010363 phase shift Effects 0.000 description 3
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000036541 health Effects 0.000 description 2
- 230000003116 impacting effect Effects 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000010355 oscillation Effects 0.000 description 2
- 230000000737 periodic effect Effects 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 229910000760 Hardened steel Inorganic materials 0.000 description 1
- 238000013016 damping Methods 0.000 description 1
- 238000005553 drilling Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000003203 everyday effect Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 229910001092 metal group alloy Inorganic materials 0.000 description 1
- 238000003801 milling Methods 0.000 description 1
- 239000000203 mixture Substances 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000004080 punching Methods 0.000 description 1
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D11/00—Portable percussive tools with electromotor or other motor drive
- B25D11/06—Means for driving the impulse member
- B25D11/12—Means for driving the impulse member comprising a crank mechanism
- B25D11/125—Means for driving the impulse member comprising a crank mechanism with a fluid cushion between the crank drive and the striking body
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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
- B25D2217/0088—Arrangements for damping of the reaction force by use of counterweights being mechanically-driven
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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
- B25D2250/245—Spatial arrangement of components of the tool relative to each other
Abstract
The invention relates to a power tool (7) comprising a percussion assembly (8), an eccentric shaft (32) for driving the percussion assembly, and a counterweight (2) for compensating vibrations of the power tool caused in particular by the percussion assembly. The counterweight (2) at least partly surrounds the eccentric shaft (32).
Description
Technical field
The present invention relates to a kind of electric tool, it comprises beater mechanism assembly, for driving the eccentric shaft of beater mechanism assembly and the balance mass for the vibration that compensates electric tool.
Background technology
Because the workload that allows will be associated with the health load acted on operator coming into force of this laws and regulations requirement every day when using electric tool, at electric tool, especially in hammer drill and jump bit, vibrating theme and become more and more important.
When hammering the impact drilling of machine into shape and cutter cuts, the maximum health load of user comes from through the housing vibration that beater mechanism produces.Just, in large hammer drill and jump bit, due to high impact energy, vibration is given prominence to very much.Therefore, for the user of these machines, the working time of permission is not having the serious minimizing in situation lower part ground of other measure.Therefore, under developmently more and more to make an effort in such solution, the vibration of electric tool is reduced in these solutions.Can ensure thus, also can continue to work with this utensil without restriction.
Fig. 1 illustrates the typical housing vibration 100 produced in the vibration of the housing of hammer drill and jump bit 7, and the vibration of housing is caused by beater mechanism assembly 8, and wherein impulse member 81 is driven by centering type piston gear 12.Horizontal axis 101 illustrates angle of revolution [unit °], vertical axis 102 illustrates the skew [unit mm] of housing.Vibrative housing vibration 100 is made up of multiple frequency content.Basic frequency is derived by the cycle acceleration of impulse member 81.But Fig. 1 illustrates: the skew caused by the cycle acceleration of impulse member 81 with from other vibration source, such as from impacting not superposed by other frequency of the gravity compensated of the impact of chain and anti-impact process and driver.Because housing vibration 100 is not substantially sinusoidally extend with basic frequency, but other frequency content changes curve combining with the sinusoidal with basic frequency.
Because nonlinear system works with only harmonious conditionally motion change process, each vibration component superposes in a complex manner.By the gap between all parts, by nonlinear Flexible change curve, by nonlinear impact process and the non-harmonious housing vibration by obtaining higher-order from the only harmonious approx reagency of beater mechanism.
In practice, the generation of resisting the counter-force of housing vibration realizes by dashpot or anti-vibrator.
Dashpot is the spring mass system with fixing resonant frequency, by it only can near resonant frequency among a small circle in realization to vibrate significantly reduction.
In anti-vibrator, balance mass is coupled with the drive unit of electric tool and is driven in this wise, makes the reagency produced by the driving of anti-vibrator resist vibration source as well as possible.
The driving design of the known balance mass for anti-vibrator is divided into two kinds: balance mass is forced to drive by centering type bent axle or crosshead crankshaft transmission device in the first case.
In the second situation, balance mass is by actuated by cams, and wherein, required touching contact is set up by loading the spring of balance mass.Balance mass is not forced to drive in this case.
Document EP 1 475 190 A2 and EP 1 439 038 A1 illustrates the example forcing the balance mass driven.In EP 1 475 190 A2, balance mass arranges around hammer pipe and is driven by the connecting rod connected with beater mechanism eccentric part added.Balance mass that is foursquare in EP 1 439 038 A1, that be provided with lateral slit is arranged on above eccentric part.Running in lateral slit relative to the bolt of rotation axis off-center of beater mechanism eccentric part, makes balance mass be driven by crosshead reciprocating mechanism.
Document WO 2004/082897 A1 illustrates the example by spring-loaded balance mass.In order to enable balance mass follow the tracks of cam geometry in the structure shown here, by flexible spring element, significant thrust must be applied in balance mass.What this not only needed to add expends, structure space and cost.And enhance friction and wear effect by additional spring compression, in addition most of energy loss that the compression of spring is necessary is fallen, make gross efficiency be deteriorated and more motor power must be provided.
The something in common of known embodiment is up to now, and balance mass arranges distant from vibration source.Therefore the very long and efficiency that the is decay that can be reached by balance mass of line of force distance is reduced.
Summary of the invention
Therefore, task of the present invention is, a kind of electric tool with the balance mass of vibration for electric tool of decaying is provided, this balance mass closely and very cost advantages can be arranged on the inaccessible of electric tool and have in the region of fewer parts, it can very accurately be located, and can realize the decay of improvement by this balance mass.
This task is solved by a kind of electric tool, this electric tool comprises beater mechanism assembly, for driving the eccentric shaft of beater mechanism assembly and the balance mass for the vibration caused by beater mechanism assembly that compensates electric tool, wherein, described balance mass surrounds described eccentric shaft at least in part.This at least in part around in the layout for driving the eccentric shaft of beater mechanism assembly to arrange in balance mass, minimum for the line of force distance compensating the beater mechanism drive unit causing vibration.Therefore, the decay that can realize is best.
Preferably, balance mass has dead slot, and eccentric shaft is through this dead slot.In this embodiment, balance mass in all sides all around encirclement eccentric shaft.Therefore balance mass is arranged in the inaccessible region of electric tool, but does not hinder the driving to eccentric shaft.
Beater mechanism assembly preferably includes the connecting rod with impulse member, wherein, connecting rod and eccentric shaft spaced apart and can be driven around this eccentric shaft prejudicially, wherein, that the harmonious rotary motion of eccentric shaft is converted to the cycle of impulse member on impact direction, substantially harmonious motion.Harmonious motion is the rotary motion of the fundamental frequency with substantial constant in the sense of the present invention.In harmonious sliding motion in the sense of the present invention, place change in time has unifrequent sine-shaped change curve substantially.At this, statement " substantially " relates to by the effect caused that rubs.In non-harmonious sliding motion in the sense of the present invention, place has multifrequency change curve along with the change of time.
In a preferred embodiment, the drive unit for driven equilibrium quality is not arranged on eccentric shaft rotatably.Therefore, the drive unit and also have balance mass simultaneously to be driven thus when beater mechanism assembly is driven.Therefore the drive unit of balance mass is integrated in centering type driver.
Preferably, drive unit is made with eccentric shaft integratedly.Relative to the solution of multi-piece type, such as have the solution of the drive unit be press fit on eccentric shaft, the embodiment of integral type has advantage, and the structure space namely taken when identical eccentricity is few, because do not need to maintain minimum wall thickness (MINI W.).
By the rotation of drive unit around eccentric shaft, balance mass can substantially move back and forth in the movement direction from initial point and return to initial point in a preferred embodiment.In this embodiment, balance mass is substantially axially back and forth driven periodically by drive unit.At this, the direction of motion preferably transverse to driving axis, extend at this eccentric axis, particularly preferably substantially towards or impact direction against the impulse member of beater mechanism assembly extend.
Preferably, balance mass is driven in this wise, and it is performed substantially relative to the vibration that the beater mechanism assembly counter-cyclical carries out.At this preferably, the vibration carried out relative to the beater mechanism assembly counter-cyclical in order to compensate only approximate harmonious reagency and towards beater mechanism assembly vibration phase shift carry out.Technical staff understands, and the vibration carried out of counter-cyclical of balance mass can be vibrated with other of the frequency content for compensating the vibration from other vibration source and be superposed, and the motion of balance mass is carried out with discording.These vibration sources are such as impact gap between the impact of chain and other non-counter-balanced weight of anti-impact process and drive unit, disharmonic motion change process, all parts and nonlinear Flexible change curve.
Particularly preferably, drive unit is at least partially disposed in the dead slot of balance mass.Therefore, the face mating reaction to dead slot gauge of drive unit and balance mass.Preferably, balance mass positive and/or force closure ground are coupled with drive unit, and the additional component do not produced for driven equilibrium quality is expended.In addition, the size of drive unit preferably adapts to the size of balance mass.
Preferably, balance mass is forced when drive unit drives to drive, even if make the Movement transmit between drive unit and balance mass also be clear and definite when high reagency and high running frequency.In addition, in such embodiment, the driving-energy added, additional structure space and the additional cost for other hold down gag, such as spring is not needed.Such drive unit can realize very high dynamic.Also contact mating member can not be made in addition to be lifted away from.
In addition preferably, balance mass extends on planar ground substantially, makes balance mass especially can closely be manufactured by a metal or metal alloy sheet material and in electric tool, take few structure space.Preferably, balance mass is formed by metallic plate punching.In conversion, balance mass also can be sintered.Such balance mass can very cost advantages ground be manufactured.
In an advantageous manner according to required weight and the material used, the size of balance mass on the direction of eccentric axis can be very flat and/or very little in the size in a lateral direction relative to eccentric shaft, makes balance mass can adapt to the installation situation in space.Therefore balance mass also can be integrated in existing electric tool, because almost without any need for additional structure space.Equally preferably, the Mass Distribution of balance mass can adapt to the Mass Distribution of electric tool, makes Mass Distribution by suitably selecting can compensation vibration composition, and these vibration components cause especially by the different Mass Distribution in electric tool.
In another preferred embodiment, electric tool has eccentric disc, in particular for driving beater mechanism assembly, eccentric disc in particular for drive link, this eccentric disc is not arranged on eccentric shaft rotatably, wherein, eccentric shaft is rotatably supported in bearing group zoarium by clutch shaft bearing, and wherein balance mass is arranged between eccentric disc and bearing group zoarium.Preferably, balance mass is bearing in bearing group zoarium.The layout of balance mass between eccentric disc and bearing group zoarium has advantage, and namely friction condition is very favorable, especially in the bearing group zoarium be made up of hardened steel, because this layout is arranged in the lubricating place of electric tool.Therefore balance mass is arranged in the region of the perfect lubrication of electric tool all the time, and can not produce additional expending.Therefore, be introduced in vibration source annex by the power of balance mass and carry out, namely direct on eccentric disc and very near carrying out with impacting axis.Another advantage be this layout closely, the overall structure of simple and cost advantages.In addition, balance mass can realize the good compensation of the quality to air cushion power and not compensated in this arrangement, causes the reduction of capacity eccentric bearing load thus.
Preferably, eccentric shaft is rotatably supported in the beater mechanism housing of beater mechanism assembly by the second bearing in addition, and wherein, bearing group zoarium is arranged in beater mechanism housing.
In another preferred embodiment, drive unit is made with eccentric disc integratedly.Or in another preferred embodiment, eccentric shaft, eccentric disc and drive unit are made integratedly.
Also preferably, bearing group zoarium limits the direction of motion of balance mass, especially on its lateral surface, such as, by chute guider.Equally preferably, bearing group is fit is limited in its side back to eccentric disc by the direction of motion of balance mass.Equally preferably, the direction of motion of eccentric disc limiting balance quality.Very little tolerance chain is obtained by this device.
In a kind of embodiment of conversion, the direction of motion of balance mass is limited by holding element, and this holding element is arranged in bearing group zoarium and/or is arranged on housing.Such holding element is such as the plastic components of U-shaped, this plastic components receiving balance quality and being led to balancing component by this holding element.
Drive unit preferably includes cam, this cam in order to driven equilibrium quality with dead slot mating reaction.There is this balance mass of dead slot and the cam for driving can manufacture with known measure cost advantages very much.
In a preferred embodiment, cam curve shape ground is formed, make disharmonic motion change process that can be realized balance mass by this layout, and except the vibration caused by beater mechanism assembly, also can compensate the vibration caused by other vibration source of electric tool thus at least in part.The curved profile of cam determines numerical value and the direction of the skew of balance mass significantly.Therefore, by the adaptation of profile, especially its slope, not only realize the repeatedly of reciprocating vibration of balance mass in a drive cycle inside of drive unit but also realize one or more rest points of balance mass.Therefore, this profile can realize, and makes the motion of balance mass accelerate and perform impact process by balance mass.Equally, this profile can realize the time of moving forward and the backward extension of balance mass.Therefore, the acceleration of the vibration processes of not only phase shift but also acceleration and impact process, such as beater mechanism assembly and impact process can very well be compensated.The adaptation of profile can make the motion of balance mass adapt to the vibration ratio of electric tool easily, makes it possible to realize extraordinary vibration damping.
In another preferred embodiment, drive unit comprises at least one coupling device, and wherein, this balance mass comprises at least one pairing coupling device, wherein, this coupling device in order to driven equilibrium quality with pairing coupling device mating reaction.The driving possibility of multiple other positive for balance mass and/or force closure ground mating reaction can be realized with the setting of the coupling device of pairing coupling device mating reaction.
Drive unit is preferably eccentric disc at this.Therefore, except also for driving the eccentric disc of beater mechanism assembly, do not need other drive unit, component expended, assembly cost and required structure space minimum.
In order to coupling device with pairing coupling device slip ratio and rolls than optimization, coupling device and/or match coupling device can be provided with whirligig, such as sleeve, wheel or rotatable bearing.
Also preferably, coupling device is groove and matches coupling device is the bolt be coupled in groove, and vice versa.Equally preferably, coupling device is arm and matches coupling device is groove around acting on arm, and vice versa.These embodiments can by the coupling device given prominence to relative to a face or pairing coupling device with realizes outstanding device relative to the pairing coupling device of a face sedimentation or the mating reaction of coupling device and is coupled in the device of sedimentation or the device that realizes sedimentation makes use around the device ring given prominence to, make the motion change process ensureing to determine.Implement groove or arm by shaped form, the almost arbitrary motion change curve of balance mass can be realized.The numerical value of the skew of balance mass is determined basically by curved profile at this.Therefore, by curved profile, can superposing with other component motion relative to the antiperiodic motion of the periodic motion of beater mechanism assembly of balance mass, makes it possible to the disharmonic vibration component compensating electric tool.
In another preferred embodiment, drive unit comprises at least two and takes bolt as coupling device, and wherein, balance mass comprises at least two and takes swing arm as pairing coupling device.In this case, the coupling device given prominence to relative to a face and the same pairing coupling device mating reaction relative to a face sedimentation.
At this, also ensure the motion change process determined, its mode takes bolt alternately to take one respectively and take swing arm.This driving of balance mass and step-by-step driving device act on similarly, make it possible to compensate disharmonic vibration component by balance mass.The dead slot of balance mass is determined by the position taking bolt on drive unit and by the length and profile of taking swing arm.
In another preferred embodiment, take bolt and be arranged on the cam of drive unit, this cam engagement is in the dead slot of balance mass, and wherein, cam also has curved profile.In this embodiment, the skew of balance mass taking bolt and taking swing arm and determine not by means of only mating reaction, and determined by the profile of cam.
Technical staff understands, and also can be realized the change of the skew of balance mass, and therefore, it is possible to realize disharmonic sliding motion of balance mass by the adaptation of the profile of the dead slot to balance mass.
In electric tool according to the present invention, effectively, very economical space saving and therefore balance mass can be integrated in extremely difficult close region to compensate the vibration of electric tool cost advantages.By the adaptation of the profile to drive unit and/or balance mass, except the vibration that the substantially harmonious sliding motion in the cycle by impulse member causes, also can compensate the vibration caused by other vibration source.
Accompanying drawing explanation
By accompanying drawing, the present invention is described below.Accompanying drawing is only exemplary and does not limit general design of the present invention.
Fig. 1 illustrates the typical housing vibration produced when the vibration of the housing of hammer drill and jump bit,
Fig. 2 to 4 illustrates a part of the electric tool with beater mechanism assembly respectively, wherein, electric tool is hammer drill at this, and the wherein vertical section of electric tool 7 shown in Figure 2, the top view of the eccentric disc of electric tool 7 shown in Figure 3, and Fig. 4 illustrates the horizontal profile of the balance mass be arranged in electric tool 7
Fig. 5 to 9 illustrates the different embodiments of balance mass and drive unit, and
Figure 10 illustrate Fig. 4 to 7 with 9 the skew relevant with the eccentric shaft anglec of rotation of balance mass.
Detailed description of the invention
As described in the preamble part of this patent application, Fig. 1 illustrates the typical housing vibration produced when the housing vibration of hammer drill and jump bit.
Fig. 2 to 4 illustrates a part for the electric tool 7 with beater mechanism assembly 8 respectively, wherein, electric tool 7 is hammer drill at this, and the wherein vertical section of electric tool 7 shown in Figure 2, the top view of the eccentric disc 10 of electric tool 7 shown in Figure 3, and Fig. 4 illustrates the horizontal profile of the balance mass 2 be arranged in electric tool 7.
Electric tool 7 drives by motor (not shown at this), and wherein, motor 7 drives the motor reel 9 with driving pinion 91, and wherein driving pinion 91 drives eccentric disc 10.This eccentric disc 10 is not arranged on eccentric shaft 32 rotatably, and this eccentric shaft can be supported around eccentric axis 33 rotationally by the first capacity eccentric bearing 61 and the second capacity eccentric bearing 62.First capacity eccentric bearing 61 is arranged in the housing 14 of beater mechanism assembly 8 and the second capacity eccentric bearing 62 is arranged in bearing group zoarium 13, and wherein, bearing group fit 13 is arranged in the housing 14 of beater mechanism assembly 8 equally itself.
Eccentric shaft 32 does not also arrange roller gear 17 rotatably, this roller gear driving clutch gear 16 and circular cone transmission device 15.Circular cone transmission device 15 drives driven gear 18, and this driven gear is arranged around the hammer pipe 19 of beater mechanism assembly 8, and this hammer pipe is driven.
Connecting rod 12 is arranged on eccentric disc 10 around eccentric axis 33 prejudicially rotationally by cam pin 11.By connecting rod 12, the rotary motion of eccentric disc 10 is converted to rectilinear motion.Therefore, connecting rod 12 drives the impulse member 81 of beater mechanism assembly 8 to do substantially harmonious sliding motion periodically.
In order to compensate the vibration of electric tool 7, this electric tool has balance mass 2.This balance mass 2 is driven by the drive unit 3 supported rotationally by around eccentric axis 33, and wherein, drive unit 3 is converted into the sliding motion of balance mass 2 around the rotary motion of eccentric axis 33.
In electric tool 7 shown here, balance mass 2 is arranged between eccentric disc 10 and bearing group zoarium 13.Drive unit 3 is cams 31, and this cam is arranged in the dead slot 21 of balance mass 2, to ensure reliable Movement transmit.Cam is not arranged around eccentric shaft 32 rotatably, makes eccentric axis 33 be driving axis of drive unit 3.Drive unit 3 and balance mass 2 are coupled thus, and balance mass 2 is driven by this drive unit forcibly when drive unit 3 rotates.
As shown in Figure 4, cam 31 has circular profile 35.This cam 31 rotates around eccentric axis 33 prejudicially when drive unit 3 rotates.Fig. 4 illustrates the eccentricity 331 of the cam 31 when drive unit 3 turns round around eccentric axis 33 part.Dead slot 21 and cam 31 so determine size, make the touching contact existed all the time when cam 31 rotates in direction of rotation 4 between cam 31 and dead slot 21.When cam 31 rotates around eccentric axis 33 prejudicially in direction of rotation 4, it is axially shifting balance quality 2 therefore.Balance mass 2 moves back and forth thus in the direction of motion 5 extended transverse to eccentric axis 33.In order to make balance mass 2 freely can move back and forth in the direction of motion 5 in electric tool 7, being provided with thereon and leaving a blank 22.
In the profile 25 of balance mass 2, the harmonious rotation of drive unit 3 causes the substantially harmonious sliding motion of balance mass 2 due to the circular contour 35 of drive unit 3 and the touching contact that exists between drive unit 3 and balance mass 2 when drive unit 3 rotates.The vibration of balance mass 2 along with the change curve 100 of time be substantially unifrequent sine-shaped.
Figure 10 a) illustrates the change curve 100 of motion of the balance mass 2 when drive unit 3 turns round 360 ° around eccentric axis, horizontal axis 101 illustrates angle of revolution [unit °], vertical axis 102 illustrates the skew [unit mm] of balance mass 2.The amplitude of the change curve 100 of the vibration of balance mass 2 is equivalent to eccentricity 331.In present case, drive unit 3 and balance mass 2 are arranged in this wise, make to there is the phase shift for the harmonious oscillating movement of the impulse member 81 of beater mechanism assembly 8.But, only can cause substantially harmonious counter-movement by this embodiment.Therefore, the decay of the vibration caused by other vibration source except the acceleration except the vibration cause of periodic motion, such as impulse member 81 is realized unsatisfactorily.
Fig. 5 to 9 illustrates the balance mass 2 of different embodiment and the embodiment of drive unit 3.The non-harmonious sliding motion of balance mass 2 can be performed, the vibration caused by many vibration sources of make can be decayed by them electric tool 7, especially housing by the embodiment listed at this.
Drive unit 3 is constructed to cam 31 in Figure 5, and this cam to be arranged on eccentric shaft 32 and can to rotate around eccentric axis 33.Cam 31 is provided with coupling device 311 prejudicially.This coupling device 311 is pin at this.Balance mass 2 has symmetrical groove as pairing coupling device 211.For Fig. 5, term pin and coupling device 311, and word slot and pairing coupling device 211 are synonymously used respectively.
Groove 211 has symmetrical V-arrangement profile 25, and this profile has the angle of attack 251.When drive unit 3 rotates in direction of rotation 4, pin 311 rotates around eccentric axis 33 prejudicially.Because groove 211 is not circular but V-arrangement, and therefore pin 311 can not freely move along groove 211, thus pin 311 at it around pressing against during eccentric axis 33 eccentric motion in balance mass 2 and axially mobile this balance mass.
Fig. 5 a) illustrates balance mass 2 when 0 ° of angle of revolution of drive unit 3 on initial point 20.Fig. 5 b) balance mass 2 after the revolution of drive unit 3 part is shown, by this part spin balancing quality 2 relative to an initial point 20 axially mobile side-play amount 201 in the direction of motion 5.
Figure 10 c) change curve 100 of the motion of the balance mass 2 of Fig. 5 when drive unit 3 turns round 360 ° around eccentric axis 33 is shown.Also angle of revolution [unit °] is shown on horizontal axis 101 here and the skew [unit mm] of balance mass 2 is shown on vertical axis 102.
In this embodiment, motion change process can be changed by the angle of attack 251 of groove 21 and the eccentricity 331 of pin 31.This embodiment can as at Figure 10 c) as shown in realize the motion steeper relative to Fig. 2 to 4---respective acceleration amplitude and quiescent phase.
In order to realize balance mass 2 freely moving back and forth in electric tool 7, this balance mass 2 also has leaves a blank 22.The eccentric disc 10 of such as electric tool 7 is suitable as drive unit 3, and wherein, pin 311 is arranged on eccentric disc 10 prejudicially.
The another kind of embodiment of balance mass 2 shown in Figure 6 and drive unit 3.Fig. 6 a) illustrates top view, and Fig. 6 b) section by line A-A is shown.Drive unit 3 is implemented as circular cam 31.Drive unit 3 is provided with first take bolt 311 and second and take bolt 312 as coupling device 311,312.Balance mass 2 have first take swing arm 211 and second take swing arm 212 as pairing coupling device 211,212, they extend in the dead slot 21 of balance mass 2 at this.Dead slot 21 itself determines size in this wise, makes the motion of balance mass 2 unaffected.
First takes bolt 311 is arranged in this wise, it is entered when drive unit 3 rotates in direction of rotation 4 and to contact with the first touching taking swing arm 211 and drive balance mass 2 and balance mass is axially moved in the direction of motion 5, contact with the first touching taking swing arm 211 until its departs from.Second takes bolt 312 is arranged in this wise, make it take swing arm 212 with second when drive unit 3 rotates in direction of rotation 4 to touch and contact and drive and shifting balance quality 2 in the contrary direction of motion 5, contact with the second touching taking swing arm 212 until its departs from.Take swing arm 211,212 and take bolt 311,312 and arrange in this wise in addition, make them one after the other enter touching contact and contact with the touching that comes off.Therefore, when drive unit 3 turns round 360 °, balance mass 2 travels forward once and back moves once again.
Figure 10 e) change curve 100 of the motion of the balance mass 2 of Fig. 6 when drive unit 3 turns round 360 ° around eccentric axis 33 is shown.Horizontal axis 101 illustrates again angle of revolution [unit °] and the skew [unit mm] of balance mass 2 is shown on vertical axis 102.
In this embodiment, by taking bolt 311,312 and taking quantity and the position of swing arm 211,212 and motion change process can be changed by the profile 25 taking swing arm 211,212.
Have cam 31 similarly according to the drive unit of Fig. 7 and Fig. 2 to 4, this cam not to be arranged on rotatably on eccentric shaft 32 and can to rotate around eccentric axis 33.In order to driven equilibrium quality 2, dead slot 21 mating reaction of cam 31 and balance mass 2, its mode is that cam engagement is in the dead slot 21 of balance mass 2, be connected with making drive unit 3 and balance mass 2 positive and/or force closure, and balance mass 2 is forced drive and move back and forth in the axial direction by this drive unit when drive unit 3 rotates.
But different from the drive unit 3 of Fig. 2 to 4, the cam 31 of Fig. 7 has the profile 35 of profile 35, the i.e. equal-width curve of curve.
Similar with Fig. 5, Fig. 7 a) illustrates balance mass 2 when 0 ° of angle of revolution of drive unit 3 on initial point 20.Fig. 7 b) balance mass 2 after the revolution of drive unit 3 part is shown, balance mass 2 by the revolution of this part relative to an initial point 20 axially mobile side-play amount 201 in the direction of motion 5.
In the embodiment of Fig. 7, the harmonious rotation of drive unit 3 causes disharmonic sliding motion of balance mass 2.The vibration of balance mass 2 along with the change curve 100 of time be multifrequency.Figure 10 b) change curve 100 of the motion of the balance mass 2 when drive unit 3 turns round 360 ° around eccentric axis 33 is shown.Horizontal axis 101 illustrates angle of revolution [unit °] and the skew [unit mm] of balance mass 2 is shown on vertical axis 102.
When drive unit 3 turns round 360 ° around eccentric axis 33, the change curve 100 of the motion of balance mass 2 demonstrates the steeper gradient and quiescent phase.
Cam 31 is preferably arranged on the eccentric shaft 32 of electric tool 7.
Fig. 8 and Fig. 7 illustrates the drive unit 3 with cam 31 similarly, and wherein, balance mass 2 has dead slot 21, and cam 31 is coupled in this dead slot.
But the cam of Fig. 8 31 has other curved profile 35, and dead slot 21 also has the profile 25 of the change curve 100 of the motion affecting balance mass 2.Therefore also allow by this embodiment the approximate arbitrary motion change curve 100 realizing balance mass 2.Therefore, when drive unit 3 in direction of rotation 4 around 360 of eccentric axis 33 ° of pivotal inside, not only reverse motion but also oscillation shape can realize with multiple frequency content.
Fig. 9 illustrates a kind of embodiment, and its drive unit 3 has a groove with curved profile 35 as coupling device 311.This balance mass 2 has pin as pairing coupling device 211.Therefore, word slot and coupling device 311 and term pin and pairing coupling device 211 are synonymously used respectively for Fig. 9.
The profile 35 of the groove 311 of the drive unit 3 of Fig. 9 is variable to the distance of eccentric axis 33.Therefore, in this embodiment, the almost arbitrary motion change curve 100 of balance mass 2 can be produced.Figure 10 d) citing the change curve 100 of the motion of balance mass 2 is shown.Drive unit 3 in direction of rotation 4 around 360 of eccentric axis 33 ° of pivotal inside, the profile 35 extended by the shaped form of groove 311 can not only be realized having the counter motion of multiple frequency content and can realize having the oscillation shape of multiple frequency content.
Groove 311 is preferably arranged, such as milling is in the eccentric disc 10 of electric tool 7.Very can save space thus and expend with minimum component and drive unit 3 is integrated in electric tool 7 cost advantages very much.In order to improve the rolling ratio of pin 211 in groove 311, pin 211 such as can be provided with sleeve or rotating bearing.
For being combined with the conversion of embodiment of pin as pairing coupling device 211 using groove as coupling device 311 in groove, also following embodiment can be expected, wherein around functional element, such as there is acting on arm around ground around functional element of U-shape.
Claims (15)
1. electric tool (7), it has beater mechanism assembly (8), for driving the eccentric shaft (32) of this beater mechanism assembly (8) and the balance mass (2) for the vibration that compensates this electric tool (7), it is characterized in that, described balance mass (2) surrounds described eccentric shaft (32) at least in part, eccentric disc (10) is not arranged on described eccentric shaft (32) rotatably, and described eccentric shaft (32) is rotatably supported in bearing group zoarium (13) by clutch shaft bearing (61), wherein, described balance mass (2) is arranged between described eccentric disc (10) and described bearing group zoarium (13).
2. electric tool according to claim 1 (18), is characterized in that, described balance mass (2) has dead slot (21), and described eccentric shaft (32) is through described dead slot.
3. electric tool according to claim 2 (18), is characterized in that, in order to drive described balance mass (2), a drive unit (3) is not arranged on described eccentric shaft (32) rotatably.
4. electric tool according to claim 3 (18), is characterized in that, described drive unit (3) is at least partially disposed in the dead slot (21) of described balance mass (2).
5. the electric tool (18) any one of claims 1 to 3, is characterized in that, described balance mass (2) extends on planar ground substantially.
6. the electric tool (18) any one of claims 1 to 3, it is characterized in that, described eccentric shaft (32) is rotatably supported in the beater mechanism housing (14) of described beater mechanism assembly (8) by the second bearing (62), wherein, described bearing group zoarium (13) is arranged in described beater mechanism housing (14).
7. according to the electric tool (18) of claim 3 or 4, it is characterized in that, described drive unit (3) comprises cam (31), wherein, described cam (31) in order to drive described balance mass (2) and with described dead slot (21) mating reaction.
8. electric tool according to claim 3 (18), it is characterized in that, described drive unit (3) comprises at least one coupling device (311,312), and described balance mass (2) comprise at least one pairing coupling device (211,212), wherein, described coupling device (311,312) in order to drive described balance mass (2) and with described pairing coupling device (211,212) mating reaction.
9. electric tool according to claim 8 (18), is characterized in that, described drive unit (3) is eccentric disc (10).
10. the electric tool (18) any one of according to Claim 8 with 9, is characterized in that, described coupling device (311) is groove and described pairing coupling device (211) is coupled to the bolt in described groove, and vice versa.
Electric tool (18) any one of 11. according to Claim 8 with 9, it is characterized in that, described coupling device (311) is arm and described pairing coupling device (211) is groove around acting on described arm, and vice versa.
Electric tool (18) any one of 12. according to Claim 8 with 9, it is characterized in that, described drive unit (3) comprises at least two and takes bolt (311,312) as coupling device, and described balance mass (2) comprises at least two takes swing arm (211,212) as pairing coupling device.
13. electric tools according to claim 1 (18), is characterized in that, described balance mass is for compensating housing vibration.
14., according to the electric tool (18) of claim 1 or 13, is characterized in that, described vibration or housing vibration are caused by this beater mechanism assembly (8).
15. electric tools according to claim 1 (18), is characterized in that, described eccentric disc is the eccentric disc for driving described beater mechanism assembly (8).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE200910044938 DE102009044938A1 (en) | 2009-09-24 | 2009-09-24 | Power tool with a striking mechanism assembly and a balancing mass to compensate for vibrations of the power tool |
| DE102009044938.8 | 2009-09-24 | ||
| PCT/EP2010/060853 WO2011035955A1 (en) | 2009-09-24 | 2010-07-27 | Power tool comprising a percussion assembly and a counterweight for compensating vibrations of the power tool |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102510791A CN102510791A (en) | 2012-06-20 |
| CN102510791B true CN102510791B (en) | 2015-06-03 |
Family
ID=42985228
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201080042521.3A Expired - Fee Related CN102510791B (en) | 2009-09-24 | 2010-07-27 | Power tool comprising a percussion assembly and a counterweight for compensating vibrations of the power tool |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP2480380A1 (en) |
| CN (1) | CN102510791B (en) |
| DE (1) | DE102009044938A1 (en) |
| WO (1) | WO2011035955A1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105465271B (en) * | 2014-06-23 | 2019-02-22 | 博世电动工具（中国）有限公司 | Balance weight mechanism and electric tool |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3890708A (en) * | 1972-07-21 | 1975-06-24 | Metabowerke Kg | Compass saw |
| EP0124198A1 (en) * | 1983-02-07 | 1984-11-07 | Skil Nederland B.V. | Adjustable orbital reciprocating saw |
| JPS6094281A (en) * | 1983-10-28 | 1985-05-27 | 日立工機株式会社 | Vibration reducer for striking tool |
| CN1761553A (en) * | 2003-03-21 | 2006-04-19 | 百得有限公司 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
| EP1864760A2 (en) * | 2006-06-08 | 2007-12-12 | HILTI Aktiengesellschaft | Manual machine tool with crank driven air spring striking mechanism |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4195818B2 (en) | 2003-01-16 | 2008-12-17 | 株式会社マキタ | Electric hammer |
| DE602004027011D1 (en) | 2003-03-21 | 2010-06-17 | Black & Decker Inc | Uziervorrichtung |
| DE602004026243D1 (en) | 2003-05-09 | 2010-05-12 | Makita Corp | power tool |
| WO2005105386A1 (en) * | 2004-04-30 | 2005-11-10 | Makita Corporation | Working tool |
| JP2007175839A (en) * | 2005-12-28 | 2007-07-12 | Hitachi Koki Co Ltd | Striking tool |
-
2009
- 2009-09-24 DE DE200910044938 patent/DE102009044938A1/en not_active Withdrawn
-
2010
- 2010-07-27 EP EP10740197A patent/EP2480380A1/en not_active Withdrawn
- 2010-07-27 WO PCT/EP2010/060853 patent/WO2011035955A1/en active Application Filing
- 2010-07-27 CN CN201080042521.3A patent/CN102510791B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3890708A (en) * | 1972-07-21 | 1975-06-24 | Metabowerke Kg | Compass saw |
| EP0124198A1 (en) * | 1983-02-07 | 1984-11-07 | Skil Nederland B.V. | Adjustable orbital reciprocating saw |
| JPS6094281A (en) * | 1983-10-28 | 1985-05-27 | 日立工機株式会社 | Vibration reducer for striking tool |
| CN1761553A (en) * | 2003-03-21 | 2006-04-19 | 百得有限公司 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
| EP1864760A2 (en) * | 2006-06-08 | 2007-12-12 | HILTI Aktiengesellschaft | Manual machine tool with crank driven air spring striking mechanism |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102510791A (en) | 2012-06-20 |
| DE102009044938A1 (en) | 2011-03-31 |
| EP2480380A1 (en) | 2012-08-01 |
| WO2011035955A1 (en) | 2011-03-31 |
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