CN102510791A - 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
- Publication number
- CN102510791A CN102510791A CN2010800425213A CN201080042521A CN102510791A CN 102510791 A CN102510791 A CN 102510791A CN 2010800425213 A CN2010800425213 A CN 2010800425213A CN 201080042521 A CN201080042521 A CN 201080042521A CN 102510791 A CN102510791 A CN 102510791A
- Authority
- CN
- China
- Prior art keywords
- balance mass
- electric tool
- drive unit
- coupling device
- vibration
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000009527 percussion Methods 0.000 title abstract 4
- 230000008878 coupling Effects 0.000 claims description 47
- 238000010168 coupling process Methods 0.000 claims description 47
- 238000005859 coupling reaction Methods 0.000 claims description 47
- 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 59
- 230000008859 change Effects 0.000 description 29
- 238000000034 method Methods 0.000 description 14
- 230000008569 process Effects 0.000 description 14
- 230000001133 acceleration Effects 0.000 description 7
- 230000005540 biological transmission Effects 0.000 description 5
- 230000003044 adaptive effect Effects 0.000 description 4
- 238000009826 distribution Methods 0.000 description 4
- 238000004062 sedimentation Methods 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 230000010363 phase shift Effects 0.000 description 3
- 238000009933 burial Methods 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000002349 favourable effect 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
- 229910000760 Hardened steel Inorganic materials 0.000 description 1
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 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
- 230000005484 gravity Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000005461 lubrication 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
- 238000004080 punching Methods 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
Images
Classifications
-
- 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
-
- 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
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Percussive Tools And Related Accessories (AREA)
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, the balance mass that it comprises the beater mechanism assembly, is used for the eccentric shaft of driving impact mechanism assembly and is used to compensate the vibration of electric tool.
Background technology
Since the workload that allow every day when using electric tool will with act on health load on the operator the coming into force of this laws and regulations requirement that interrelate, at electric tool, especially the vibration theme becomes more and more important in hammer drill and jump bit.
When impact drilling and the cutter of hammer machine were cut, the health load of user's maximum came from the housing that produces through beater mechanism and vibrates.Just in big hammer drill and jump bit, because high impact energy, vibration is very outstanding.Therefore, for the user of these machines, the working time of permission is not having serious minimizing the in ground, situation lower part of other measure.Therefore, under developmently more and more on such solution, work hard, the vibration of electric tool is reduced in these solutions.Can guarantee thus, also can continue to use without restriction this utensil work.
Fig. 1 is illustrated in the typical housing vibration 100 that produces in the vibration of housing of hammer drill and jump bit 7, and the vibration of housing causes that through beater mechanism assembly 8 wherein impulse member 81 drives through centering type piston gear 12.Angle of revolution [unit °] is shown on horizontal axis 101, the skew [mm of unit] of housing is shown on vertical axis 102.Vibrative housing vibration 100 is made up of a plurality of frequency contents.Basic frequency is derived by the cycle acceleration of impulse member 81.But Fig. 1 illustrates: the skew that the cycle acceleration through impulse member 81 causes with from other vibration source, for example from other frequency stack of the impact of impacting chain and the gravity that is not compensated that process and driver are hit in recoil.Because housing vibration 100 is not sinusoidally to extend with basic frequency basically, but other frequency content changes the curve stack with the sinusoidal with basic frequency.
Because nonlinear system works with only harmonious conditionally motion change process, so each vibration component superposes with the mode of complicacy.Obtain the non-harmonious housing vibration of higher-order through the gap between each parts, through nonlinear elasticity change curve, through nonlinear impact process and through only harmonious approx reagency from beater mechanism.
In practice, the generation of the counter-force of opposing housing vibration realizes by dashpot or anti-vibrator.
Dashpot is the spring mass system with fixing resonant frequency, through it only can be near resonant frequency among a small circle in realize that significant vibration reduces.
In anti-vibrator, the drive unit of balance mass and electric tool coupling and being driven in this wise makes and resists vibration source by the reagency of the driving and generating of anti-vibrator as well as possiblely.
The driving design of the known balance mass that is used for anti-vibrator is divided into two kinds: be forced driving first kind of situation balance mass by centering type bent axle or crosshead crank throw transmission device.
In second kind of situation, balance mass drives through cam, and wherein, required touching contact is set up by the spring-loaded to balance mass.Balance mass is not forced driving in this situation.
Document EP 1 475 190 A2 and EP 1 439 038 A1 illustrate the example of the balance mass of forcing driving.Balance mass is provided with and is driven by the additional connecting rod that connects with the beater mechanism eccentric part around the hammer pipe in EP 1 475 190 A2.Balance mass foursquare in EP 1 439 038 A1, that be provided with lateral slit be arranged on eccentric part above.The bolt eccentric with respect to rotation of beater mechanism eccentric part moves in lateral slit, makes balance mass pass through the crosshead reciprocating mechanism and drives.
Document WO 2004/082897 A1 illustrates the example that receives spring-loaded balance mass.In order in this structure, to make balance mass can follow the tracks of the cam geometry, must significant thrust be applied on the balance mass through flexible spring element.This not only need add expends, structure space and cost.And strengthened the friction and wear effect through additional spring compression, and fall for the necessary most of energy loss of the compression of spring in addition, make gross efficiency variation and more motor power must be provided.
The something in common of known embodiment is up to now, and balance mass is provided with distantly from vibration generation source.Therefore very long and efficient decay that can reach through balance mass of line of force distance reduces.
Summary of the invention
Therefore; Task of the present invention is; A kind of electric tool of balance mass of the vibration with the electric tool that is used to decay is provided; In the inaccessible zone with fewer parts that this balance mass can be very compactly and very cost advantageously is installed in electric tool, it can very accurately be positioned, and can realize the decay that improves through this balance mass.
This task solves through a kind of electric tool; This electric tool comprises the beater mechanism assembly, be used for the eccentric shaft of driving impact mechanism assembly and be used to compensate the balance mass of passing through the vibration that the beater mechanism assembly causes of electric tool; Wherein, said balance mass is surrounded said eccentric shaft at least in part.In this layout that is provided with around the eccentric shaft that is used for the driving impact mechanism assembly at least in part of balance mass, the line of force distance that is used to compensate the beater mechanism drive unit that causes vibration is minimum.The decay that therefore, can realize is best.
Preferably, balance mass has dead slot, and eccentric shaft passes this dead slot.In this embodiment, balance mass in all sides all around surrounding eccentric shaft.Therefore balance mass is arranged in the inaccessible zone of electric tool, but does not hinder the driving to eccentric shaft.
The beater mechanism assembly preferably includes the connecting rod that has impulse member; Wherein, Connecting rod and eccentric shaft are spaced apart and can be prejudicially be driven around this eccentric shaft, wherein, harmonious the rotatablely moving of eccentric shaft convert into the cycle of impulse member on impact direction, harmonious motion basically.Harmonious motion is to have rotatablely moving of the fundamental frequency of substantial constant on meaning of the present invention.In the harmonious sliding motion on meaning of the present invention, place change in time has unifrequent basically sine-shaped change curve.At this, statement " basically " relates to the effect that causes through friction.In the non-harmonious sliding motion on meaning of the present invention, the place is along with the change of time has multifrequency change curve.
In preferred embodiment, the drive unit that is used for the driven equilibrium quality can not be arranged on eccentric shaft with relatively rotating.Therefore, drive unit and also have balance mass to be driven simultaneously thus when the beater mechanism assembly is driven.Therefore the drive unit of balance mass is integrated in the centering type driver.
Preferably, drive unit is processed with eccentric shaft integratedly.With respect to the solution of multi-piece type, for example have the solution that is press fit into the drive unit on the eccentric shaft, the embodiment of integral type has advantage, and the structure space that promptly when identical eccentricity, takies is few, because need not keep minimum wall thickness (MINI W.).
Around the rotation of eccentric shaft, balance mass can move back and forth and return to initial point in the direction of motion in preferred embodiment a kind of from initial point basically through drive unit.In this embodiment, balance mass substantially axially back and forth drives through drive unit periodically.At this, the direction of motion is preferably transverse to driving axis, extend at this eccentric axis, preferred especially basically towards or extend against the impact direction of the impulse member of beater mechanism assembly.
Preferably, balance mass is driven in this wise, makes it carry out the vibration of carrying out with respect to the beater mechanism assembly counter-cyclical basically.At this preferably, the vibration phase shift ground towards the beater mechanism assembly carries out in order to compensate only approximate harmonious reagency in the vibration of carrying out with respect to the beater mechanism assembly counter-cyclical.The technical staff understands, the vibration carried out of the counter-cyclical of balance mass can with other vibration stack that is used to compensate from the frequency content of the vibration of other vibration source, make the motion of balance mass carry out with discording.These vibration sources for example are to impact the impact of chain and process and drive unit are hit in recoil other the not gap between counter-balanced weight, disharmonic motion change process, each parts and nonlinear elasticity change curve.
Particularly preferably, drive unit is at least partially disposed in the dead slot of balance mass.Therefore, the face mating reaction to the dead slot gauge of drive unit and balance mass.Preferably, balance mass shape sealed and/or force closure ground and drive unit coupling make that not producing the additional member that is used for the driven equilibrium quality expends.In addition, the size of drive unit preferably adapts to the size of balance mass.
Preferably, balance mass is forced driving when drive unit is driven, even if make that the motion transmission between drive unit and the balance mass also is clear and definite when high reagency and high running frequency.In addition, in such embodiment, the driving energy that need not add, additional structural space and the additional cost that is used for other hold down gag, for example spring.Such drive unit can be realized very high dynamic.The contact mating member is lifted away from.
In addition preferably, balance mass is extended basically planarly, makes balance mass especially can make and in electric tool, take few structure space very compactly by a metal or metal alloy sheet material.Preferably, balance mass is formed by metallic plate punching.Conversion ground, balance mass also can be sintered.Such balance mass very cost is advantageously made.
In an advantageous manner according to required weight and employed material; 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 with respect to eccentric shaft, makes balance mass can adapt to the installation situation in space.Therefore balance mass also can be integrated in the existing electric tool, because almost without any need for the additional structural space.Equally preferably, the mass distribution of balance mass can adapt to the mass distribution of electric tool, makes that the mass distribution through suitably selection can the compensation vibration composition, and these vibration components especially cause through the different mass distribution in the electric tool.
In another preferred embodiment; Electric tool has eccentric disc, in particular for the driving impact mechanism assembly, in particular for the eccentric disc of drive link; This eccentric disc can not be arranged on the eccentric shaft with relatively rotating; Wherein, eccentric shaft is rotatably supported in the bearing group zoarium through clutch shaft bearing, and wherein balance mass is arranged between eccentric disc and the bearing group zoarium.Preferably, balance mass is bearing in the bearing group zoarium.The layout of balance mass between eccentric disc and bearing group zoarium has advantage, and promptly friction condition is very favorable, especially in the bearing group zoarium of being processed by hardened steel, because this layout is arranged in the lubricated space of electric tool.Therefore balance mass is arranged in the zone of the perfect lubrication of electric tool all the time, and can not produce additional expending.Therefore, the power through balance mass is introduced in the vibration source annex carries out, and promptly directly on eccentric disc and very, carries out near impacting axis ground.Another advantage is very compact, the simple and favourable overall structure of cost of this layout.In addition, balance mass can realize the good compensation to the quality of air cushion power and not compensated in this arrangement, causes reducing of capacity eccentric bearing load thus.
Preferably, eccentric shaft is rotatably supported in the beater mechanism housing of beater mechanism assembly through second bearing in addition, and wherein, the bearing group zoarium is arranged in the beater mechanism housing.
In another preferred embodiment, drive unit is processed with eccentric disc integratedly.Perhaps in another preferred embodiment, eccentric shaft, eccentric disc and drive unit are processed integratedly.
Also preferably, the fit direction of motion that limits balance mass of bearing group is especially on its side, for example through the chute guider.Equally preferably, the bearing group zoarium is limited in its side back to eccentric disc with the direction of motion of balance mass.Equally preferably, the direction of motion of eccentric disc limiting balance quality.Obtain very little tolerance chain through this device.
In a kind of embodiment of conversion, the direction of motion of balance mass is through the holding element restriction, and this holding element is arranged in the bearing group zoarium and/or is arranged on the housing.Such holding element for example is the plastic components of U-shaped, this plastic components receiving balance quality and balancing component is led through this holding element.
Drive unit preferably includes cam, this cam for the driven equilibrium quality with the dead slot mating reaction.The cam that has this balance mass of dead slot and be used to drive can with known measure very cost advantageously make.
A kind of preferred embodiment in; Cam curve shape ground constitutes; Make and to realize disharmonic motion change process of balance mass, and except the vibration that causes by the beater mechanism assembly, also can compensate the vibration that the vibration source by other of electric tool causes thus at least in part through this layout.The curved profile of cam has been confirmed the numerical value and the direction of the skew of balance mass significantly.Therefore, adaptive through profile, especially its slope not only realizes the repeatedly double vibrations of balance mass but also realizes one or more rest points of balance mass in a drive cycle inside of drive unit.Therefore, this profile can be realized, makes the motion acceleration of balance mass and carries out impact process through balance mass.Equally, this profile can realize that the time of the forward and backward motion of balance mass extends.Therefore, not only the acceleration of the vibration processes of phase shift but also acceleration and impact process, for example beater mechanism assembly and impact process can very well be compensated.Profile adaptive 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 for the driven equilibrium quality with pairing coupling device mating reaction.Can realize being used for the driving possibility of the sealed and/or force closure ground mating reaction of a plurality of other shape of balance mass with the setting of the coupling device of pairing coupling device mating reaction.
Drive unit is at this eccentric disc preferably.Therefore,, do not need other drive unit, make that member expends, assembly cost and required structure space be minimum except being used for the eccentric disc of driving impact mechanism assembly yet.
For the slip ratio of coupling device and pairing coupling device with roll than optimization, coupling device and/or pairing coupling device can be provided with whirligig, for example sleeve, wheel or rotatable bearing.
Also preferably, coupling device is that groove and pairing coupling device are the bolts that is coupled in the groove, and vice versa.Equally preferably, coupling device is that arm and pairing coupling device are that vice versa around the groove that acts on arm.These embodiments can be through the motion change process that realizes that with respect to the outstanding coupling device of a face or pairing coupling device and mating reaction with respect to the pairing coupling device of a face sedimentation or coupling device outstanding device is coupled in the device of sedimentation or realize that the device of sedimentation makes usefulness around outstanding device ring, make guaranteeing confirming.Implement groove or arm through shaped form ground, can realize the almost motion change curve arbitrarily of balance mass.The numerical value of the skew of balance mass is confirmed through curved profile at this basically.Therefore, through curved profile, the antiperiodic motion of the periodic motion with respect to the beater mechanism assembly of balance mass can superpose with other component motion, makes it possible to compensate disharmonic vibration component of electric tool.
In another preferred embodiment, drive unit comprises that at least two are taken bolt as coupling device, and wherein, balance mass comprises that at least two are taken swing arm as the pairing coupling device.In this situation, the coupling device and same pairing coupling device mating reaction with respect to a face sedimentation outstanding with respect to a face.
At this, the motion change process of also guarantee confirming, its mode are to take bolt alternately to take one respectively and take swing arm.This driving and the step-by-step movement transmission device of balance mass act on similarly, make it possible to compensate disharmonic vibration component through balance mass.The dead slot of balance mass is confirmed through the position of taking bolt on the drive unit and through length and the profile of taking swing arm.
In another preferred embodiment, to take on the cam that bolt is arranged on drive unit, this cam is coupled in the dead slot of balance mass, and wherein, cam also has curved profile.In this embodiment, the skew of balance mass is not only through the taking bolt and take swing arm and confirm of mating reaction, and confirms through the profile of cam.
The technical staff understands, and through the adaptive change that also can realize the skew of balance mass to the profile of the dead slot of balance mass, and therefore can realize disharmonic sliding motion of balance mass.
In electric tool according to the present invention, balance mass can save very effectively, very much for the vibration that compensates electric tool space ground and therefore cost advantageously be integrated in the extremely difficult approaching zone.Adaptive through to the profile of drive unit and/or balance mass also can compensate the vibration that causes through other vibration source except the vibration that the harmonious basically sliding motion in the cycle through impulse member causes.
Description of drawings
By accompanying drawing the present invention is described below.Accompanying drawing only is exemplary and does not limit general design of the present invention.
The typical housing vibration that Fig. 1 produces when being illustrated in the vibration of 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 a hammer drill at this, and wherein in the vertical section of electric tool shown in Fig. 27, at the vertical view of the eccentric disc of electric tool shown in Fig. 37; And Fig. 4 illustrates the horizontal profile that is arranged on the balance mass in the electric tool 7
Fig. 5 to 9 illustrate balance mass and drive unit different embodiments and
Figure 10 illustrates the skew relevant with the eccentric shaft anglec of rotation of Fig. 4 to 7 and 9 balance mass.
The specific embodiment
As as described in the preface of this patent application part, the typical housing that Fig. 1 produces when being illustrated in the housing vibration of hammer drill and jump bit vibrates.
Fig. 2 to 4 illustrates the part of the electric tool 7 with beater mechanism assembly 8 respectively; Wherein, Electric tool 7 is a hammer drill at this; And wherein in the vertical section of electric tool shown in Fig. 27, at the vertical view of the eccentric disc 10 of electric tool shown in Fig. 37, and Fig. 4 illustrates the horizontal profile of the balance mass 2 that is arranged in the electric tool 7.
Electric tool 7 drives by motor (not shown at this), and wherein, motor 7 drives the motor reel 9 that has driving pinion 91, and wherein driving pinion 91 drives eccentric disc 10.This eccentric disc 10 can not be arranged on the eccentric shaft 32 with relatively rotating, and this eccentric shaft can be supported around eccentric axis 33 by first capacity eccentric bearing 61 and second capacity eccentric bearing 62 rotationally.First capacity eccentric bearing 61 is arranged in the housing 14 of beater mechanism assembly 8 and second capacity eccentric bearing 62 is arranged in the bearing group fit 13, and wherein, bearing group fit 13 itself is arranged in the housing 14 of beater mechanism assembly 8 equally.
On eccentric shaft 32, also roller gear 17 can not be set with relatively rotating, this roller gear drives clutch gear 16 and circular cone transmission device 15.Circular cone transmission device 15 drives driven gear 18, and this driven gear is provided with around the hammer pipe 19 of beater mechanism assembly 8, makes that this hammer pipe is driven.
Connecting rod 12 is arranged on the eccentric disc 10 around eccentric axis 33 by cam pin 11 prejudicially rotationally.Convert rotatablely moving of eccentric disc 10 into rectilinear motion through connecting rod 12.Therefore, the impulse member 81 of connecting rod 12 driving impact mechanism assemblies 8 is done harmonious basically sliding motion periodically.
In order to compensate the vibration of electric tool 7, this electric tool has balance mass 2.This balance mass 2 drives by the drive unit that is supported rotationally around eccentric axis 33 3, and wherein, drive unit 3 is converted into the sliding motion of balance mass 2 around rotatablely moving of eccentric axis 33.
In the electric tool 7 here, balance mass 2 is arranged between eccentric disc 10 and the bearing group fit 13.Drive unit 3 is cams 31, and this cam is arranged in the dead slot 21 of balance mass 2, to guarantee that motion is transmitted reliably.Cam can not be provided with around eccentric shaft 32 with relatively rotating, makes that eccentric axis 33 is driving axis of drive unit 3.Drive unit 3 is coupled with balance mass 2 thus, makes balance mass 2 when drive unit 3 rotations, driven by the strong hand by this drive unit.
As shown in Figure 4, cam 31 has circular profile 35.This cam 31 rotates around eccentric axis 33 when drive unit 3 rotations prejudicially.The eccentricity 331 of cam 31 when Fig. 4 is illustrated in drive unit 3 around the revolution of eccentric axis 33 parts.Dead slot 21 is so confirmed size with cam 31, makes when cam 31 rotates, to have the touching contact between cam 31 and the dead slot 21 all the time on direction of rotation 4.When cam 31 on direction of rotation 4 during prejudicially around eccentric axis 33 rotation, it is shifting balance quality 2 axially therefore.Balance mass 2 moves back and forth on the direction of motion 5 of extending transverse to eccentric axis 33 thus.For balance mass 2 can freely be moved back and forth on the direction of motion 5 in electric tool 7, be provided with above that and leave a blank 22.
In the profile 25 of balance mass 2, the harmonious rotation of drive unit 3 is because the touching contact of the circular contour 35 of drive unit 3 and existence between drive unit 3 and balance mass 2 when drive unit 3 rotations causes the harmonious basically sliding motion of balance mass 2.The vibration of balance mass 2 is along with change of time curve 100 is unifrequent basically sine-shaped.
Figure 10 is the change curve 100 of the motion of balance mass 2 when being illustrated in drive unit 3 around 360 ° of eccentric axis revolutions a), and angle of revolution [unit °] is shown on horizontal axis 101, and the skew [mm of unit] of balance mass 2 is shown on vertical axis 102.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 is provided with balance mass 2 in this wise, the feasible phase shift that has the harmonious oscillating movement of the impulse member 81 that is used for beater mechanism assembly 8.But, only can cause harmonious basically anti-motion through this embodiment.Therefore, the decay to the vibration that except that the acceleration of the vibration cause of periodic motion, for example impulse member 81, causes through other vibration source realizes unsatisfactorily.
Fig. 5 to 9 illustrates the balance mass 2 of different embodiments and the embodiment of drive unit 3.Can carry out the non-harmonious sliding motion of balance mass 2 through the embodiment of listing at this, make through their can the decay vibration that many vibration sources cause of passing through of electric tool 7, especially housing.
Groove 211 has the V-arrangement profile 25 of symmetry, and this profile has the angle of attack 251.When drive unit 3 rotated on direction of rotation 4, pin 311 was prejudicially around eccentric axis 33 rotations.The V-arrangement because groove 211 is not circular, and sell 311 and therefore can not freely move along groove 211 presses against on the balance mass 2 during around eccentric axis 33 eccentric motions and axially moves this balance mass at it so sell 311.
Fig. 5 is the balance mass 2 on initial point 20 when being illustrated in 0 ° of angle of revolution of drive unit 3 a).Fig. 5 b) is illustrated in drive unit 3 parts revolution balance mass 2 afterwards, axially on the direction of motion 5, moves a side-play amount 201 with respect to initial point 20 through this partial rotation balance mass 2.
The change curve 100 of the motion of the balance mass 2 of Fig. 5 when Figure 10 c) being illustrated in drive unit 3 around 360 ° of eccentric axis 33 revolutions.Here also angle of revolution [unit °] is being shown on the horizontal axis 101 and the skew [mm of unit] of balance mass 2 is being shown on vertical axis 102.
In this embodiment, the angle of attack 251 through groove 21 and sell 31 eccentricity 331 and can change the motion change process.This embodiment can be as at Figure 10 c) shown in realize motion---separately acceleration amplitude and the quiescent phase steeper with respect to Fig. 2 to 4.
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.For example the eccentric disc 10 of electric tool 7 is suitable as drive unit 3, and wherein, pin 311 is arranged on the eccentric disc 10 prejudicially.
Another kind of embodiment at balance mass shown in Fig. 62 and drive unit 3.Fig. 6 a) illustrates vertical view, and Fig. 6 b) section through line A-A is shown.Drive unit 3 is implemented as circular cam 31.On drive unit 3, being provided with first takes bolt 311 and second and takes bolt 312 as coupling device 311,312.Balance mass 2 has first to be taken swing arm 211 and second and takes swing arm 212 as pairing coupling devices 211,212, and they extend in the dead slot 21 of balance mass 2 at this.Dead slot 21 itself is confirmed size in this wise, makes that the motion of balance mass 2 is unaffected.
First takes bolt 311 is provided with in this wise; Make it when drive unit 3 rotates on direction of rotation 4, get into first take swing arm 211 touching contact and drive balance mass 2 and balance mass is axially moved on the direction of motion 5, up to its break away from and first take swing arm 211 touching contact.Second takes bolt 312 is provided with in this wise; Make it when drive unit 3 rotates on direction of rotation 4 with second take swing arm 212 touching contact and drives and on the opposite direction of motion 5 shifting balance quality 2, the touching of taking swing arm 212 up to its disengaging and second contacts.Take swing arm 211,212 and take bolt 311,312 setting in this wise in addition, make them one after the other get into the touching contact and contact with the touching that comes off.Therefore, when 360 ° of drive unit 3 revolutions, balance mass 2 travels forward once and again toward swivel motion once.
The change curve 100 of the motion of the balance mass 2 of Fig. 6 when Figure 10 e) being illustrated in drive unit 3 around 360 ° of eccentric axis 33 revolutions.Angle of revolution [unit °] is being shown again on the horizontal axis 101 and the skew [mm of unit] of balance mass 2 is being shown on vertical axis 102.
In this embodiment, through taking bolt 311,312 and taking quantity and the position of swing arm 211,212 and can change the motion change process through the profile 25 of taking swing arm 211,212.
Drive unit and Fig. 2 to 4 according to Fig. 7 have cam 31 similarly, and this cam can not be arranged on the eccentric shaft 32 with relatively rotating and can rotate around eccentric axis 33.For driven equilibrium quality 2; Dead slot 21 mating reactions of cam 31 and balance mass 2; Its mode is that cam is coupled in the dead slot 21 of balance mass 2; Make drive unit 3 and/or force closure sealed ground be connected, and balance mass 2 is forced to drive and reciprocating motion in the axial direction when drive unit 3 rotations by this drive unit with balance mass 2 shapes.
But different with the drive unit 3 of Fig. 2 to 4, the cam 31 of Fig. 7 has the profile 35 of curve, is the profile 35 of equal-width curve.
Similar with Fig. 5, Fig. 7 is the balance mass 2 on initial point 20 when being illustrated in 0 ° of angle of revolution of drive unit 3 a).Fig. 7 b) be illustrated in drive unit 3 parts revolution balance mass 2 afterwards, balance mass 2 axially moves a side-play amount 201 through this part revolution with respect to initial point 20 on 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 is along with change of time curve 100 is multifrequency.The change curve 100 of the motion of balance mass 2 when Figure 10 b) being illustrated in drive unit 3 around 360 ° of eccentric axis 33 revolutions.Angle of revolution [unit °] is being shown on the horizontal axis 101 and the skew [mm of unit] of balance mass 2 is being shown on vertical axis 102.
The change curve 100 of the motion of balance mass 2 demonstrates the steeper gradient and quiescent phase when drive unit 3 turns round 360 ° around eccentric axis 33.
Cam 31 preferably is arranged on the eccentric shaft 32 of electric tool 7.
Fig. 8 and Fig. 7 illustrate 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 that influences balance mass 2.Therefore also allow to realize the approximate motion change curve 100 arbitrarily of balance mass 2 through this embodiment.Therefore, when drive unit 3 360 ° of rotating inside around eccentric axis 33 on direction of rotation 4, not only reverse motion but also oscillation shape can realize with a plurality of frequency contents.
Fig. 9 illustrates a kind of embodiment, and its drive unit 3 has a groove that has shaped form 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 terms pin and pairing coupling device 211 are used with the free burial ground for the destitute 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, can produce the almost motion change curve 100 arbitrarily of balance mass 2.Figure 10 d) change curve 100 of the motion of balance mass 2 is shown for example.Drive unit 3 on direction of rotation 4 around 360 ° of rotating inside of eccentric axis 33, the oscillation shape that the profile 35 that extends through the shaped form of groove 311 not only can be realized having the counter motion of a plurality of frequency contents and can realize having a plurality of frequency contents.
Groove 311 preferably is provided with, for example milling is in the eccentric disc 10 of electric tool 7.Can save very much the space thus and expend very that cost advantageously is integrated in drive unit 3 in the electric tool 7 with the member of minimum.In order to improve the rolling ratio of pin 211 in groove 311, pin 211 can for example be provided with sleeve or rotating bearing.
For with groove as coupling device 311 and in groove, be combined with the conversion of embodiment of pin as pairing coupling device 211; Also can expect following embodiment, wherein around functional element, for example have acting on the arm around ground of U-shaped shape around functional element.
Claims (13)
1. electric tool (7); It has beater mechanism assembly (8), be used to drive the eccentric shaft (32) of this beater mechanism assembly (8) and be used to compensate the vibration of this electric tool (7), the balance mass (2) of housing vibration especially; This vibration or housing vibration especially cause through this beater mechanism assembly (8); It is characterized in that said balance mass (2) is surrounded said eccentric shaft (32) at least in part.
2. according to the electric tool (18) of claim 1, it is characterized in that said balance mass (2) has dead slot (21), said eccentric shaft (32) passes said dead slot.
3. according to each electric tool (18) in the above claim, it is characterized in that in order to drive said balance mass (2), a drive unit (3) can not be arranged on the said eccentric shaft (32) with relatively rotating.
4. according to each electric tool (18) in the above claim, it is characterized in that said drive unit (3) is at least partially disposed in the dead slot (21) of said balance mass (2).
5. according to each electric tool (18) in the above claim, it is characterized in that said balance mass (2) is extended basically planarly.
6. according to each electric tool (18) in the above claim; It is characterized in that; Eccentric disc (10), can not be arranged on the said eccentric shaft (32) in particular for the eccentric disc that drives said beater mechanism assembly (8) with relatively rotating; And said eccentric shaft (32) is rotatably supported in the bearing group zoarium (13) through clutch shaft bearing (61), and wherein, said balance mass (2) is arranged between said eccentric disc (10) and the said bearing group fit (13).
7. according to each electric tool (18) in the above claim; It is characterized in that; Said eccentric shaft (32) is rotatably supported in the beater mechanism housing (14) of said beater mechanism assembly (8) through second bearing (62); Wherein, said bearing group fit (13) is arranged in the said beater mechanism housing (14).
8. according to each electric tool (18) in the above claim, it is characterized in that said drive unit (3) comprises cam (31), wherein, said cam (31) in order to drive said balance mass (2) with said dead slot (21) mating reaction.
9. according to each electric tool (18) in the claim 1 to 7, it is characterized in that said drive unit (3) comprises at least one coupling device (311; 312), and said balance mass (2) comprise at least one the pairing coupling device (211,212); Wherein, Said coupling device (311,312) in order to drive said balance mass (2) with said pairing coupling device (211,212) mating reaction.
10. according to the electric tool (18) of claim 9, it is characterized in that said drive unit (3) is eccentric disc (10).
11. according to each electric tool (18) in the claim 9 and 10, it is characterized in that said coupling device (311) is that groove and said pairing coupling device (211) are the bolts that is coupled in the said groove, vice versa.
12., it is characterized in that said coupling device (311) is that arm and said pairing coupling device (211) are that vice versa around the groove that acts on the said arm according to each electric tool (18) in the claim 9 and 10.
13. according to each electric tool (18) in the claim 9 and 10; It is characterized in that said drive unit (3) comprises that at least two are taken bolt (311,312) as coupling device; And said balance mass (2) comprises that at least two are taken swing arm (211,212) as the pairing coupling device.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102009044938.8 | 2009-09-24 | ||
| 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 |
| 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 true CN102510791A (en) | 2012-06-20 |
| CN102510791B 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) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105465271A (en) * | 2014-06-23 | 2016-04-06 | 博世电动工具（中国）有限公司 | Counterweight mechanism and electric tool |
Citations (6)
| 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 |
| US20080029282A1 (en) * | 2004-04-30 | 2008-02-07 | Makita Corporation | Power Tool |
Family Cites Families (4)
| 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 |
| EP1818141B1 (en) | 2003-03-21 | 2010-05-12 | Black & Decker, Inc. | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
| DE602004026243D1 (en) | 2003-05-09 | 2010-05-12 | Makita Corp | power tool |
| JP2007175839A (en) * | 2005-12-28 | 2007-07-12 | Hitachi Koki Co Ltd | Impact tool |
-
2009
- 2009-09-24 DE DE200910044938 patent/DE102009044938A1/en not_active Withdrawn
-
2010
- 2010-07-27 WO PCT/EP2010/060853 patent/WO2011035955A1/en active Application Filing
- 2010-07-27 EP EP10740197A patent/EP2480380A1/en not_active Withdrawn
- 2010-07-27 CN CN201080042521.3A patent/CN102510791B/en not_active Expired - Fee Related
Patent Citations (6)
| 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 |
| US20080029282A1 (en) * | 2004-04-30 | 2008-02-07 | Makita Corporation | Power Tool |
| EP1864760A2 (en) * | 2006-06-08 | 2007-12-12 | HILTI Aktiengesellschaft | Manual machine tool with crank driven air spring striking mechanism |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105465271A (en) * | 2014-06-23 | 2016-04-06 | 博世电动工具（中国）有限公司 | Counterweight mechanism and electric tool |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2011035955A1 (en) | 2011-03-31 |
| DE102009044938A1 (en) | 2011-03-31 |
| CN102510791B (en) | 2015-06-03 |
| EP2480380A1 (en) | 2012-08-01 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| USRE33733E (en) | Device for driving a drilling and/or impacting tool | |
| EP2018939B1 (en) | Power tool with vibration damping mechanism | |
| CN102510792B (en) | Link drive with additional oscillator | |
| CN101568410B (en) | Electric hand power tool | |
| US20120192438A1 (en) | Reciprocating power tool | |
| CN101535007B (en) | Mass oscillating unit for hand-held machine tools with a striking device | |
| SE533039C2 (en) | Handheld tiger saw | |
| US9415453B2 (en) | Reciprocating tool | |
| CN101341006B (en) | Hand power tool, in particular drill hammer and/or chipping hammer | |
| CN101096086A (en) | A hammer drill and method for indicating the beat piece wear | |
| CN102230518B (en) | Drum-type inner ring plate speed reducer with less tooth difference | |
| CN102510791A (en) | Power tool comprising a percussion assembly and a counterweight for compensating vibrations of the power tool | |
| CN110118250A (en) | A kind of switching mechanism of chain-crankshaft linkage | |
| CN202349134U (en) | Gear and rack transmission device capable of eliminating wear clearance | |
| CN202318260U (en) | Electric tool and transmission switching mechanism thereof | |
| CN102667221A (en) | Controlled oscillation damper | |
| CN201925420U (en) | Two-stage planet-gear speed reducer | |
| CN104985567A (en) | Novel composite impact drill | |
| CN101117997A (en) | Internal tricyclic decelerator | |
| CN103347653B (en) | Blade clamping apparatus | |
| US4278295A (en) | Impacting rock breaker | |
| CN202469360U (en) | End face sealing device of hydrostatic testing machine | |
| CN102105273B (en) | Impact device | |
| CN201386766Y (en) | Pin tooth transmission mechanism with pin sleeve | |
| CN203730232U (en) | Anti-eccentric-abrasion guide device and mortar pump |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20150603 Termination date: 20170727 |