CN101104261B - Vibration reduction apparatus for power tool and power tool incorporating such apparatus - Google Patents
Vibration reduction apparatus for power tool and power tool incorporating such apparatus Download PDFInfo
- Publication number
- CN101104261B CN101104261B CN 200710128304 CN200710128304A CN101104261B CN 101104261 B CN101104261 B CN 101104261B CN 200710128304 CN200710128304 CN 200710128304 CN 200710128304 A CN200710128304 A CN 200710128304A CN 101104261 B CN101104261 B CN 101104261B
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- China
- Prior art keywords
- piston
- gear
- hammer
- mass body
- bearing structure
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/28—Counterweights, i.e. additional weights counterbalancing inertia forces induced by the reciprocating movement of masses in the system, e.g. of pistons attached to an engine crankshaft; Attaching or mounting same
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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
- B25D2211/00—Details of portable percussive tools with electromotor or other motor drive
- B25D2211/06—Means for driving the impulse member
- B25D2211/068—Crank-actuated impulse-driving mechanisms
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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
- B25D2217/0084—Arrangements for damping of the reaction force by use of counterweights being fluid-driven
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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
- B25D2217/00—Details of, or accessories for, portable power-driven percussive tools
- B25D2217/0073—Arrangements for damping of the reaction force
- B25D2217/0076—Arrangements for damping of the reaction force by use of counterweights
- B25D2217/0092—Arrangements for damping of the reaction force by use of counterweights being spring-mounted
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
- B25D—PERCUSSIVE TOOLS
- B25D2250/00—General details of portable percussive tools; Components used in portable percussive tools
- B25D2250/045—Cams used in percussive tools
-
- 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
- B25D2250/391—Use of weights; Weight properties of the tool
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Percussive Tools And Related Accessories (AREA)
- Drilling And Boring (AREA)
Abstract
A vibration reduction apparatus (501) for use with a hammer tool having a hammer piston (520) is shown. The hammer piston (520) is caused to reciprocate in cylinder (530) by rotation of a gear wheel (523) about axis (524), the hammer piston (520) being mounted to the gear wheel (523) via piston arm (531) and pivot pin (522). Reciprocating motion of the hammer piston causes a flying mass (569) to be driven along cylinder (530) to impart a hammer action to a bit of the tool. The gear wheel (523) is caused to rotate about axis (524) by meshing of gear (514) on drive shaft (511) with gear teeth (532) on the periphery of gear wheel (524), the drive shaft (511) being caused to rotate by a motor (not shown) of the tool. A cam (533) is rigidly mounted around gear wheel (523), a counterweight (521) surrounds piston cylinder (530), and a cam follower (534) is provided on counterweight (521). The cam follower (534) on counterweight (521) is urged into contact with cam (533) by means of a compression spring (535). The external profile of the cam (533) is such that rotation of gear wheel (534) to cause reciprocating motion of hammer piston (520) causes oscillation of counterweight (521) relative to piston cylinder (530) in antiphase to motion of the hammer piston (520) to counteract vibrations produced by operation of the hammer action of the tool.
Description
Divide an application
The application is dividing an application of No. 200480007676.8 applications, and the applying date of No. 200480007676.8 applications is on March 19th, 2004, and denomination of invention is " the vibration damping equipment of power tool and the power tool of this equipment is housed ".
Technical field
The present invention relates to be used for the vibration damping equipment and the power tool that this equipment is housed of power tool.The present invention especially but not exclusively relate to the vibration damping equipment that is used for power hammer and the power hammer that this equipment is housed.
Background technology
Electrically operated hammer is known, and wherein the actuator of moving mass body (flying mass) form is back and forth driven in piston, and the moving mass body transmits hammer action to the impact of this pistons end to hammer bit (bit ofthe hammer).This device is disclosed in the European patent application EP 1252976 and shown in Fig. 1.
With reference to figure 1, the stamping hammer of prior art comprises motor 2, is contained in geared system and piston driver in the metal gear housing 5 that is centered on by plastic casing 4 in detail.The back handle shell that back handle 6 and trigger switch device 8 are installed is installed in the rear portion of housing 4,5.The cable (not shown) extends through cable guide device 10 and this motor is connected in external power source.When this cable is connected in external power source, push trigger switch device 8, motor 2 startings are to drive the armature of this motor rotatably.Radial fan 14 is installed in an end of this armature and forms pinion in the opposite end of this armature, and this armature drives this fan and this pinion rotatably during with this electric motor starting of box lunch.The 5 usefulness magnesium manufacturings of metal gear housing also have the steel plug-in unit, and support rigidly and hold parts within it.
This motor pinion drives first gear of idler gear device rotatably, and this idler gear device is rotatably installed on the axle, and this axle is installed in the plug-in unit of this gear housing 5.This idler gear has second gear, and this second gear drives a travelling gear rotatably.This travelling gear non-rotatably is installed on the transmission spindle, and this axle is installed in this gear housing 5.Crankshaft cheek 30 non-rotatably is installed in the end of this transmission spindle away from this travelling gear, and this crankshaft cheek is formed with the eccentric orfice that is used to hold eccentric crank pin 32.This crank-pin 32 stretches into the hole of these crank arm 34 rear ends from this crankshaft cheek, so that this crank arm can pivot around this crank-pin 32.The relative front end of this crank arm 34 has the hole, stretches out a gudgeon pin 36 through this hole, so that this crank arm 34 can pivot around this gudgeon pin 36.This gudgeon pin 36 is installed in the rear portion that is installed in this piston 38 in the receiving opening that forms in a pair of relative arm through the two ends with this gudgeon pin 36, wherein relative arm reaches piston 38 rear portions.This piston is installed in the columniform hollow mandrel 40 with reciprocating mode, so that it can move back and forth in this hollow mandrel.O-ring packing 42 is installed in the annular groove on the circumference that is formed at this piston 38, between this piston 38 and this hollow mandrel 40 inner surfaces, to form gas-tight seal.
When motor 2 startings, this armature pinion drives this idler gear device rotatably through first gear, and second gear of this idler gear device drives this transmission spindle rotatably through this travelling gear.This transmission spindle drives this crankshaft cheek 30 rotatably, and comprises that the crank arm device of crank-pin 32, crank arm 34 and gudgeon pin 36 will change the reciprocal driving to this piston 38 into from the rotation driving of crankshaft cheek 30.By this way, when the user through pushing trigger switch 8 during actuating motor 2, piston 38 drives before and after reciprocally along this hollow mandrel.
Space in this gear housing 5 is communicated with the space outerpace of this hammer with filter 11 through narrow groove 9.Therefore, the air pressure in this hammer that changes along with the temperature of this hammer equals this hammer air outside pressure.Filter 11 also keeps the air ratio in this hammer gear housing 5 totally not have dust.
But such known hammer drill (hammer drill) has shortcoming, i.e. hammering action produces sizable vibration, and is harmful to the user of this equipment, and can produce damage to equipment itself.
Known to absorbing material is set can reduce the influence of vibration to the user of this power tool on every side at implement handle, this absorbing material plays the effect of passive damping material.But the effect that the minimizing of this material passes to the equipment user vibration is limited.
Active vibration damping equipment is known, and wherein a plurality of rotatable mass are driven around corresponding rotating shaft, and the barycenter and the rotating shaft of these a plurality of rotatable mass are spaced apart, makes these mass produce vibration around the rotation of rotating shaft.Relative phase between the speed through controlling these mass and the barycenter of these mass, the vibrational energy that is produced are enough in offsets undesired vibration, for example, and the vibration in the Diesel engine.This device is disclosed among FR 2606110, WO88/06687, FR 2550471, EP 0840191, EP 0505976 and the EP 0337040.But, up to the present, these technology are used for reducing undesirable vibration that power tool produces are not considered to practicable as yet.
DE3427342 discloses a kind of hammer drill, wherein is installed in the reciprocating motion that oscillating deck driver on the axle causes the moving mass body, impact is passed to this drill bit (drill bit).This oscillating deck driver has the finger piece that engages piston; This piston forms the part of hammer mechanism; Therefore the rotation of this oscillating deck axle mounted thereto causes the reciprocating motion of this piston, and is arranged on this and goes up the vibration that this equipment generation is offset on balance mass body portion ground on end relative with this finger piece.
GB 2256905 discloses a kind of reciprocating-type saw, and wherein first and second oscillating decks reciprocally drive saw blade and balance mass respectively, so that the vibration that saw produces is minimum.But the shortcoming of this saw is to be provided with the pair of swing plate just is difficult to construct compactly saw.
Summary of the invention
The preferred embodiments of the present invention are intended to overcome the above-mentioned shortcoming of prior art power tool.
According to an aspect of the present invention; A kind of power hammer equipment vibration damping equipment that is used for is provided; This power hammer equipment comprises housing, is arranged on the motor in this housing, is suitable for causing that by this motor motion is to realize pistons reciprocating in the hole; With the moving mass body that is arranged in this hole; So that make the said reciprocating motion of said piston in said hole in use cause the reciprocating motion of said moving mass body with respect to this housing, impact is passed to the operation element of this hammer equipment, this vibration damping equipment comprises at least one drivable mass; It is suitable for being centered around at least in part at least a portion in this hole; And wherein, at least one said drivable mass is suitable for being caused moving back and forth by this motor, so that offset the vibration of the said housing that is caused with respect to the reciprocating motion of this housing by this moving mass body at least in part.
Through providing at least one to be suitable for to be centered around at least in part the drivable mass of at least a portion in this hole; Wherein at least one said drivable mass makes and is suitable for being caused to move back and forth by this motor; So that offset the vibration of the said housing that causes with respect to the reciprocating motion of this housing by this moving mass body at least in part; The advantage that provides like this is to make the structure of power hammer equipment compact more, and reduces to greatest extent simultaneously because the operation of this power hammer equipment imposes on the twisting moment of this housing.
This equipment can also comprise at least one travelling gear, is suitable for by said motor-driven, with the motion that causes said moving mass body and cause at least one said said reciprocating motion that drives mass.
This vibration absorber also can comprise cam gear, and this cam gear can rotate through at least one travelling gear, and is suitable for engaging at least one said mass that drives.
This equipment can also comprise first bias unit, is used at least one said mass that drives is pushed to said cam gear and engages.
This equipment can also comprise cam follow-up device, is used for changing rotatablely moving of said cam gear at least one said reciprocating motion that drives mass.
This bias unit can be suitable at least one said mass that drives is pushed to said cam follow-up device and engages.
This cam follow-up device can comprise at least one notch, and it is suitable for being received at least one said corresponding convexity that drives on the mass.
The advantage that provides like this is to be convenient to this drivable mass and this cam follow-up device breaks away from.
When power hammer equipment and workpiece broke away from, this drivable mass or each said drivable mass can be suitable for moving and break away from and the engaging of this cam gear.
This equipment can also comprise holding device, is used for when power hammer equipment and workpiece disengaging, keeping this drivable mass or each said drivable mass to break away from said cam gear.
This holding device can comprise sealing device, and it is suitable between the operation element of this power hammer equipment and this housing, moving.
This equipment can also comprise disabling device, is used to make said vibration damping equipment failure.
Said disabling device can comprise the device that is used to make said cam gear and the disengaging of said motor.
Said disabling device can comprise locking device, is used at least one said drivable mass on the throne with respect to this housing locking.
At least one said drivable mass can be driven by the air that said moving mass body moves.
This equipment can also comprise sensing device, is used to detect the phase place and/or the amplitude of the vibration that is produced by said vibration damping equipment.
This equipment can also comprise adjusting device, is used to regulate the phase place and/or the amplitude of the vibration that is produced by said vibration damping equipment.
This equipment can also comprise control device, is used to respond the said adjusting device of said sensing devices control.
This equipment can also comprise at least one support member; Be used to support at least one drivable mass; And be suitable for causing to move back and forth by this motor; Wherein this at least one said drivable mass said drive the reciprocating motion of mass during relatively and at least one said support member be slidably, and this equipment also comprises second bias unit, is used for said drivable mass is pushed to at least one said support member engaging.
At least one said support member can comprise sleeve, is used for centering at least in part at least a portion in said hole.
This equipment can also comprise buffer unit, but is used to cushion the impact between at least one drive unit and at least one the said support member.
According to a further aspect in the invention, a kind of power hammer equipment is provided, it comprises:
Housing;
Be arranged on the motor in this housing;
Be suitable for causing piston in the hole, to move back and forth by said motor;
Be arranged on the moving mass body in this hole, it makes the reciprocating motion of said piston in said hole cause the reciprocating motion of said moving mass body with respect to said housing in use, impact is passed to the operation element of this power hammer equipment; And
Vibration damping equipment as defined above.
This equipment can also comprise the piston barrel that limits said hole.
At least one said drivable mass can be suitable for forming at least a portion of said piston barrel.
The advantage that is provided like this is that this power hammer equipment can manufacture compact structure more.
This equipment can also comprise that at least one is arranged on the convexity on the said piston barrel, is used to engage the cam follower means of said vibration damping equipment.
At least one said convexity can be arranged on the inner surface of said piston barrel.
The advantage that is provided like this is the cramped construction that more helps this equipment.
This equipment can also comprise sensor device, is used for detecting by vibrative phase place of said vibration damping equipment and/or amplitude.
This equipment can also comprise control device, is used to respond said sensor device and controls said adjusting device.
This equipment can also comprise drive unit, is used to make at least one drivable mass and/or said piston to produce and moves back and forth.
Said drive unit can comprise the axle that is suitable for by said motor rotation; Actuator with bonding part; This bonding part is used for saidly driving mass and/or said moving mass body engages with at least one, and the balance mass body that departs from diameter ground, said bonding part relative position.
According to another aspect of the invention; A kind of vibration damping equipment that is used for power tool is provided, and this power tool comprises housing, is arranged on the motor in this housing; Be suitable for causing the motion of at least one first operation element of this instrument; This vibration damping equipment comprises at least one pair of rotatable mass, and this comprises the corresponding first and second rotatable mass to rotatable mass or every pair of said rotatable mass, and they are suitable for along mutually opposite direction around the rotation of separately first and second rotating shafts; Wherein, each said first and second gyrating mass body has and the isolated barycenter separately of corresponding said rotating shaft.
At least one said right said first and second mass can comprise gear separately.
At least one said right said gear can be meshing with each other.
At least one said right gyrating mass body can be installed with one heart.
The advantage that provides like this is to make vibration absorber have more compact structure.
This vibration damping equipment can also comprise adjusting device, is used to regulate the phase place and/or the amplitude of the vibration that is produced by said vibration damping equipment.
This equipment can also comprise at least one travelling gear, and it is suitable for by said motor-driven, with the motion that causes at least one said first operation element and drive said vibration damping equipment.
The advantage that provides like this is to guarantee that this vibration absorber is driven with the frequency identical with first operation element of this instrument.
Said adjusting device can comprise the device that is used for respect at least one said at least one said travelling gear of first operation element rotation.
Said adjusting device can comprise and is used to make at least one said right said mass relative to each other to rotate the device of predetermined angular.
In accordance with a further aspect of the present invention, a kind of power tool is provided, comprises:
Housing;
Be arranged on the motor in this housing, it is suitable for causing the motion at least one first operation element of this instrument; With
Vibration damping equipment as defined above.
This motor can be suitable for driving at least one said first operation element through at least one said right said rotatable mass.
At least one said drivable mass can be suitable for forming at least a portion of said piston barrel.
The advantage that provides like this is to make this equipment have more compact structure.
This equipment can also comprise that at least one is arranged on the convexity on the said piston barrel, is used to engage the cam follow-up device of said vibration damping equipment.
At least one said convexity can be arranged on the inner surface of said piston barrel.
The advantage that provides like this is the further compactness that helps this device structure.
This equipment can also comprise sensor device, is used to detect vibration phase and/or the amplitude that is produced by said vibration damping equipment.
This equipment can also comprise control device, is used to respond said sensor device and controls said adjusting device.
This equipment can also comprise drive unit, be used to cause at least one said drivable mass with/obtain the reciprocating motion of said piston.
This drive unit can comprise the axle that is suitable for by said motor rotation; Actuator with the bonding part that is adapted to couple to a few said drivable mass and/or said moving mass body, and the balance mass body that departs from said bonding part diameter relative position.
In accordance with a further aspect of the present invention, a kind of actuator that is used for power tool is provided, this power tool comprises housing; Motor in this housing, and be suitable for by this motor-driven operation element, this actuator comprises bonding part and at least one balance mass body; Wherein, This actuator is adapted to be mounted to axle, so that the rotation of this axle causes the reciprocating motion of said bonding part in use, and at least one said balance mass body is positioned at and deviates from the relative position of diameter, said bonding part.
This actuator can also comprise the circular body part that is suitable for being installed on the axle, and wherein, said bonding part is elongated and extends from said main part.
Description of drawings
Below with reference to accompanying drawing, and only do not have any qualification ground description the preferred embodiments of the present invention by means of instance, wherein:
Fig. 1 is the cutaway view of prior art stamping hammer local excision;
Fig. 2 is the vibration damping equipment oblique view of first embodiment of the invention;
Fig. 3 is the exploded perspective view of the vibration damping equipment of second embodiment of the invention;
Fig. 4 is the oblique view of the vibration damping equipment of third embodiment of the invention;
Fig. 5 is the oblique view of the vibration damping equipment of fourth embodiment of the invention;
Fig. 6 is the sectional side view of the vibration damping equipment of fifth embodiment of the invention;
Fig. 7 is the cutaway view of the vibration damping equipment of sixth embodiment of the invention corresponding to Fig. 6;
Fig. 8 is the sectional view of the vibration damping equipment of seventh embodiment of the invention corresponding to Fig. 6;
Fig. 9 is the exploded perspective view of the vibration damping equipment of eighth embodiment of the invention;
Figure 10 is the oblique view of the vibration damping equipment local excision of nineth embodiment of the invention;
Figure 11 is the partial cutaway view of the vibration damping equipment of tenth embodiment of the invention corresponding to Figure 10;
Figure 12 is the partial cutaway view of the vibration damping equipment of eleventh embodiment of the invention;
Figure 13 A and 13B illustrate vibration damping equipment simulating performance shown in Figure 12;
Figure 14 illustrates the data that the simulation of Figure 13 A and 13B draws;
Figure 15 is the exploded cutaway view of the vibration damping equipment of twelveth embodiment of the invention corresponding to Figure 12;
Figure 16 is the exploded cutaway view of the vibration damping equipment of thriteenth embodiment of the invention corresponding to Figure 12;
Figure 17 is the section plan of the equipment of Figure 16;
Figure 18 is the vibration damping equipment side cutaway view of fourteenth embodiment of the invention;
Figure 19 A is the cutaway view of the oscillation bearing that uses with the present invention; And
Figure 19 B is the view corresponding to the prior art oscillation bearing of Figure 19 A.
The specific embodiment
With reference to figure 2, can cooperate the damper mechanism 101 that uses to comprise a pair of roughly the same gear 102,103 that is installed on the common axis 104 with the hammer of the stamping hammer of for example prior art shown in Figure 1 etc.Each gear 102,103 comprises the gear face with helical teeth 105 and is arranged on the pouring weight 106 on these gear 102,103 circumference.Pouring weight 106 makes the whole barycenter of each gear 102,103 deviate from the rotation through common axis 104.The helical teeth 105 of gear 102,103 each other in the face of and with bevel gear 107 engagements, make wheel 108 rotate along the direction of the arrow A in Figure 2 and cause that gear 103 rotates along arrow B through bevel gear 107.Bevel gear 107 is freely rotated with respect to stepper motor 108 along arrow C, but the adjusting of the relative position of the pouring weight 106 of gear 102,103 can be through being realized by the stepper motor 108 edges direction rotation bevel gear 107 opposite with arrow C.
The operation of damper mechanism shown in Figure 2 will be described below.
Rotatablely moving of each gear 102,103 barycenter can be resolved into the sinusoidal motion of barycenter along the pair of vertical axle on a plane perpendicular to common axis 104.Through through motor 108 changing the angular distance of pouring weight 106 on the gear 102,103, the synthesis phase of the vibration that is produced by vibration damping equipment 101 and amplitude can be adjusted to offset at least in part by the hammering that passes to this tool bit through the moving mass body and move the vibration of caused hammer housing.
With reference to figure 3, wherein, the parts identical with Fig. 2 embodiment are with identical but increase by 100 Reference numeral and represent.Hammer piston 220 drives through the cam pin on the gear plate 202 212.Gear plate 202 is co-axially mounted on the axle 207 with gear plate 203, and gear plate 203 has pouring weight 206.The gear teeth 205 on the gear plate 202,203 and bevel gear 207 engagements, this bevel gear 207 is rotated by stepper motor 208.To be similar to the mode of Fig. 2 embodiment, pouring weight 206 rotates to regulate gear plate 202,203 with respect to the rotation of the angle position mat bevel gear 207 of cam pin 212 relative to one another.
In the embodiment shown in fig. 3, being rotated the vibration that gear 203 produced by the vibration that motion produced of hammer piston 220 subdues.Diameter ground is relative haply for pouring weight 206 on gear 203 peripheries and the pin 212 on another gear 202.
With reference to figure 4, wherein identical with Fig. 3 embodiment parts are with identical but increase by 100 Reference numeral and represent, gear 302,303 is installed on the common axis (not shown) and each all has the gear teeth 305.Gear 302 has cam pin 312, and being used for driving reciprocal output shaft (not shown), this reciprocal output shaft is used for driving and is similar to hammer piston shown in Figure 3.Gear 303 has pouring weight 306 on its periphery; Make that the rotation of its barycenter and gear 303 is spaced apart; And gear 302,303 is driven shaft 310,311 drivings respectively independently of each other; This driving shaft 310,311 has gear 313,314 separately, gear 313,314 respectively with 305 engagements of the tooth of gear 302,303.
The hammering action makes moving mass body impacting tube end of body be passed to the drill bit of this instrument through the reciprocating motion of hammer piston.Driving shaft 310 makes cam pin 312 rotations; Axle 311 is also driven; Make gear 303 with gear 302 identical frequencies but opposite direction rotation, the selection of the phase difference between pouring weight 306 and the cam pin 312 is so that farthest offset the vibration that the hammering action by this instrument is produced by the vibration that rotation produced of gear 303.
With reference to figure 5; Wherein identical with Fig. 4 embodiment parts are with identical but increase by 100 Reference numeral and represent; Fig. 5 discloses a kind of vibration damping equipment 401; Be used to reduce the vibration that the reciprocating motion by hammer piston 420 causes, this hammer piston drives again and is used to produce the moving mass body (not shown) that hammering is moved.Vibration damping equipment 401 is provided with counterweight block 421, and counterweight block 421 is used for doing with hammer piston 420 haply the reciprocating motion of anti-phase.Hammer piston 420 is connected in crank arm 423 through pivot pin 422, and crank arm 423 rotates around axis 424 by means of the driving shaft (not shown) that is connected with the hammer motor.Actuating arm 425 is connected with crank arm 423 at pivotal axis 426 places, make crank arm 423 around the rotation of axis 424 cause counterweight block 421 with the reciprocating motion of hammer piston 420 same frequencys, but phase place is roughly opposite.
Gear 403 have eccentric weight 406 and have with driving shaft 411 on the external teeth 405 of gear 414 engagement.This driving shaft 411 can make gear 403 with respect to crank arm 423 rotations, makes the pouring weight 406 and the relative angle position of counterweight block 421 to transfer.As a result, the phase place of resultant vibration and amplitude can be according to the changes of the vibration of the barycenter of hammer piston 420 and according to the moving mass body, be conditioned by the case hardness of hammering and other factors.
With reference to figure 6, wherein identical with Fig. 5 embodiment parts are with identical but increase by 100 Reference numeral and represent that Fig. 6 shows a kind of compact more vibration damping equipment 501, and vibration damping equipment 501 can use with the instrument with hammer piston 520.These hammer piston 520 mat gears 523 cause the reciprocating motion in cylindrical shell 530 around the rotation of axis 524, and hammer piston 520 is installed on the gear 523 through piston arm 531 and pivot pin 522.The reciprocating motion of hammer piston 520 causes that moving mass body 569 is driven along cylindrical shell 530, the hammering action is passed to the drill bit (not shown) of this instrument.
This damper mechanism 501 has the cam of installing around gear 523 rigidly 533, the balance mass body 521 that centers on piston barrel 530, and the Cam Follower 534 on this balance mass body 521.Cam Follower 534 on this balance mass body 521 is compressed spring 535 and promotes to contact with cam 533.The exterior contour of this cam 533 make the rotation of the reciprocating gear 534 cause hammer piston 520 cause balance mass body 521 with the vibration of the phase place of the reverse movement of hammer piston 520 with respect to piston barrel 530.Because hammer piston 520 is driven by same driving shaft 511 with balance mass 521, this guarantees that this balance mass body 521 is to be driven with these hammer piston 520 identical frequencies.Because balance mass body 521 is around this cylindrical shell 530, so this damper mechanism 501 can manufacture compactlyer, and minimized by the twisting moment that operation produced of this mechanism.
For when gear 523 in rotation and the hammering of this instrument action when stopping using (for example when the drill bit of this instrument when workpiece is pulled down) can make this damper mechanism 501 ineffective; This balance mass body 521 is locked on the throne, as shown in Figure 6 at it from position farthest, the left side with respect to cylindrical shell 530.This is to realize that through in housing 537, aliging with groove 539 in these balance mass body 521 outer surfaces around the ball bearing 536 of this piston barrel 530 this ball bearing 536 allows these balance mass bodies 521 to slide with respect to piston barrel 530 usually.For when ball bearing 536 aligns with groove 539 that this balance mass body 521 is on the throne with respect to these piston barrel 530 lockings; Pin 538 right sides that move to as shown in Figure 6; The result; This ball bearing 536 be moved upwards up to this balance mass body 521 on groove 539 engage, to prevent moving axially of this balance mass body 521.In this position, cam 533 freely rotates on gear 523, but Cam Follower 534 is prevented from moving to cam 533 and engages.
With reference to figure 7; Wherein identical with Fig. 6 embodiment parts are with identical but increase by 100 Reference numeral and represent; Sixth embodiment of the present invention damper mechanism 601 has cam 633, and it is locked in gear 623 by means of pin 640 usually rigidly, and this pin is promoted downwards by torsion spring 641; As shown in Figure 7, this pin promote again ball bearing 642 to the outside of pin 640 so that lobe plate 633 is locked in gear 623.
For damper mechanism 601 is failed, the effect that overcomes compression spring 643 is shifted pin 638 onto the left side, and is as shown in Figure 7, so that make move up therefore ball bearing 642 of pin 640 can be contained in narrow 644 of pin 640.As a result, cam 633 can freely rotate on gear 623, and therefore, cam 633 is translating cam follower 634 not.Therefore balance mass body 621 does not move relative to piston barrel 630.
Fig. 8 illustrates the seventh embodiment of the present invention, and wherein identical with Fig. 7 embodiment parts are with identical but increase by 100 Reference numeral and represent.This damper mechanism 701 has balance mass body 721, and it is arranged in the chamber 750 of adjacent piston cylindrical shell 730.Hammer piston 720 is back and forth driven by the oscillating deck 751 that is installed on the driving shaft 752 (this driving shaft 752 is connected in motor); And this hammer piston 720 mobile in piston barrel 730 causes that piston barrel 730 moves with air in the groove 753 that is connected this piston barrel 730 and chamber 750, thereby causes the mobile of balance mass body 721 and the 720 basic anti-phases of hammer piston.
With reference to figure 9, wherein identical with Fig. 7 embodiment parts are with identical but increase by 200 Reference numeral and represent that cam 833 is installed on gear plate 823, and Cam Follower 834 is installed on pivotal arm 860.Pivotal arm 860 pivots around pivot pin 861, and is pushed to cam 833 by spring 835 and engages.Balance mass body 821 slidably is installed on piston barrel 830 through pin 862, and hammer piston 820 is installed on gear 823 through crank arm 831 and cam pin 822.Gear (not shown) on these hammer piston 820 driven shafts drives with the reciprocating motion mode; Tooth 832 engagements of gear on this driving shaft and gear 823; And the rotation of gear 823 and cause the reciprocating motion of balance mass body 821 with the cam 833 of Cam Follower 834 engagement, the phase place of this motion is opposite basically with the motion phase of hammer piston 820.
Balance mass body 821 is installed on the pin 820 through ball bearing 842, and this ball bearing 842 is pushed to groove 863 engagements with this pin 862 bottoms, and this pin 862 is received in the hole 864 of balance mass body 821 by means of pin 840.In order to make this damper mechanism 801 ineffective, the effect that this pin 840 overcomes compression spring 841 is pushed down, and the ball bearing 842 and the groove 863 of pin 862 are broken away from.This makes pin 862 to be free to slide in the hole 864 of this balance mass body 821.
The damper mechanism 901 of the compactness of nineth embodiment of the invention is shown in Figure 10, and wherein identical with Fig. 9 embodiment parts are with identical but increase by 100 Reference numeral and represent.Hammer piston 920 is driven by gear plate 923, this gear plate 923 have with driving shaft 911 on the tooth 932 of gear 914 engagements.Cam 933 is installed in rigidly on the gear 923 and by the inner surface of Cam Follower plate 934 and meshes.This Cam Follower plate 934 is connected in balance mass body 921 through pin 970, and this balance mass body forms the part of piston barrel 930, so the rotation of cam 933 causes balance mass body 921 vibration vertically.
In order to make this vibration damping equipment 901 inefficacies, Cam Follower plate 934 shown in figure 10 moving down so that the cam face of Cam Follower plate 934 and cam 933 are broken away from.By this way, the rotation of gear plate 923 does not cause moving axially of balance mass body 921.
With reference to Figure 11; Wherein identical with Figure 10 embodiment parts are with identical but increase by 100 Reference numeral and represent; Cam Follower 1034 usefulness spring (not shown) are pushed to and are meshed with cam 1033 and are supported by yoke plate 1075, and this yoke plate pivots and distribution 1070 is connected in the balance mass body 1021 that forms piston barrel 1030 parts around pivot 1076.Cam Follower is biased to cam 1033 and is meshed by compression spring 1077, and vibration damping equipment 1001 overcomes the effect of compression spring 1077, loses efficacy through balance mass body 1021 is moved to the left side shown in Figure 11.
Figure 12 illustrates the 11st embodiment of the present invention, and wherein identical with Figure 11 embodiment parts are with identical but increase by 100 Reference numeral and represent.Cam 1133 is installed on pin 1181 through the hole with bearing 1180, makes the rotation of crank 1182 cause the rotation of cam 1133 around rotating shaft 1183.Bearing 1184 is installed on 1121 the pin 1170 of cylindrical shell housing, make when this cylindrical shell housing 1121 when arrow D direction is pushed, this bearing 1184 contacts with the circumferential surface of cam 1133.Therefore because crank 1182 rotation driven plunger 1120, cause be mounted for relative to this tool housing (not shown) slidably cylindrical shell housing 1121 move, its phase place is opposite with piston 1120.Piston 1120 mobile in cylindrical shell 1121 causes moving of tup 1169.Ram 1186 usefulness springs 1187 are installed on the end of cylindrical shell housing 1121, and have the O shapes ring 1188 that is installed in the groove 1189 and the pair of O shape ring 1190 on its end 1191.
Figure 13 A and 13B illustrate the performance simulation of vibration damping equipment shown in Figure 12, and Simulation result is shown in Figure 14.Do not start vibration (16.5 meter per seconds that vibration damping equipment is produced
2) vibration (6.5 meter per seconds that produced during with starting vibration damping equipment
2) the equipment shown in Figure 12 of comparison shows that reduce vibration about 60%.
Figure 15 illustrates the 12nd embodiment of the present invention, and wherein identical with Figure 12 embodiment parts are with identical but increase by 100 Reference numeral and represent.The Cam Follower 1234 that has circular hole 1235 at the one of which end is around the surface of cam 1233 and be installed on this cam face; And the bearing 1236,1237 by threaded shaft 1238 remains on this cam face position on every side, and this axle 1238 is driven by gear 1239.This gear 1239 is also through arm 1220a driven plunger 1220.Hole 1240 in Cam Follower 1234 ends relative with circular port 1235 is installed on the pin 1270 on cylindrical shell 1221 lower surfaces; Make rotation through the axle 1238 of arm 1220a driven plunger 1220 also cause the rotation of cam face 1233, the rotation of cam face 1233 causes the reciprocating motion of hole 1240 and pin 1270 again.This causes the linear reciprocal movement of cylindrical shell 1221 again, the reciprocating motion anti-phase of its phase place and piston 1220.
In the equipment of Figure 15, when this tool bit (not shown) and the disengaging of workpiece (not shown), this Cam Follower 1234 does not break away from cam face 1233 or pin 1270, and therefore, damper mechanism always opens, and is allowed by the vibration that damper mechanism causes.But the structure that the advantage of the embodiment of Figure 15 is to use existing parts to greatest extent and simplifies this equipment also makes the compact conformation of this equipment simultaneously.
With reference now to Figure 16 and Figure 17; Wherein identical with Figure 15 embodiment parts are with identical but increase by 100 Reference numeral and represent; The difference of the embodiment of the 13rd embodiment of the present invention and Figure 15 is that the Cam Follower 1334 with circular hole 1335 is installed on the pin 1370 that is arranged on these piston barrel 1321 inner surfaces.As clearly visible at Figure 17, boy 1370 is arranged in the piston barrel 1321, and therefore, pin 1370 is positioned at piston 1320 back on these piston 1320 aftermost positions.This makes this equipment have compact structure more than other embodiment.
The another kind of structure of Cam Follower 1334 is shown in Figure 16, wherein, is substituted by U-lag mouth 1350 roughly in the hole 1340 of the front end of Cam Follower 1334, and this U-lag mouth 1350 is used to engage the pin 1370 that is arranged on the piston barrel 1321.When this instrument when breaking away from the similar mode of the embodiment of Figure 12 and workpiece (not shown), this notch 1350 can break away from pin 1370 with Cam Follower 1334 through the bias unit (not shown), so that make this vibration damping equipment failure.When tool bit is pushed to when engaging with workpiece, Cam Follower 1334 is pushed to pin 1370 and engages, so the entire path of pin 1370 through this hole 1340 is received in the notch 1350.
With reference to Figure 18, wherein identical with Fig. 6 embodiment parts are with identical but increase by 900 Reference numeral and represent that Figure 18 illustrates the vibration damping equipment 1401 that is used for power hammer, and this power hammer has the hammer piston 1420 that in piston barrel 1430, reciprocatingly slides.This hammer piston 1420 pivotally is installed on the gear 1423 through bar 1431 and pin 1422, and gear 1423 is installed in the bearing 1425 and has tooth 1432.Another arm 1452 is installed on the gear 1423 through pivot 1450, makes gear 1423 cause that around the rotation of axle 1424 arm 1431 and 1452 vibrates with opposite phases each other.Arm 1452 distributions 1456 pivotally are installed on the sleeve 1458, and this sleeve slidably is installed on the outer surface of piston barrel 1430.
The operation of vibration damping equipment 1401 shown in Figure 180 will be described below.
When through with 1432 engagements of the tooth on driving shaft (not shown) and the gear 1423, make gear 1423 when axle 1424 rotations, arm 1431 and 1452 moves along opposite direction each other.When hammer piston 1420 moves to the left side shown in figure 18; The air springs that are formed in the space 1470 between the moving mass body of hammering piston 1420 and ram 1469 forms into shape are initially compressed, and make ram 1469 move to the left side up to compressed air spring with mode well-known to those skilled in the art.By this way, hammer piston 1420 moves and subsequently ram 1469 has hysteresis slightly between the motion on the left side to the left side of Figure 18.
Simultaneously, arm 1452 is to right side moving sleeve 1420 shown in Figure 180.When sleeve 1458 moved right, it began to move right with respect to balance mass body 1460, and therefore, originally compression spring 1464 is compressed, and 1460 beginnings of balance mass body move right with sleeve 1458 then.In other words, sleeve 1458 initially moves right, and this sleeve 1458 moves right with balance mass 1460 after lagging behind slightly; With counterweight piston 1420 left initial movable only; Then, after lagging behind slightly, hammer piston 1420 is moved to the left with ram 1469.It is understandable that; Through suitably selecting the tensile property of compression spring 1464; Hysteresis between the motion of sleeve 1458 and balance mass 1460 can equal the hysteresis between the motion of this hammer piston 1420 and ram 1469, so the behavior of the air spring in these mechanical compression springs 1464 virtual spaces 1470.Through the behavior of coupling hammer piston 1420 and ram 1469 more nearly, the vibration in this equipment further reduces.
With reference to figure 19B, be shown specifically the oscillation bearing device with Fig. 8 of conventional structure well known to those skilled in the art.Oscillating deck 751 is installed on the axle 752 through bearing 760, when axle 752 when playing the longitudinal axis 754 rotations, so that this oscillating deck 751 can be with respect to axle 752 rotations.This oscillating deck 751 has finger piece 755, and it is used to mesh the arm of piston 720 and be arranged to and the relative balance mass body 764 in finger piece 762 diameter ground.One skilled in the art will appreciate that when axle 752 during, cause that finger piece 762 moves along this equipment longitudinal axis in complex way, so that cause the reciprocating motion of hammer piston 720 in piston barrel 730 around 754 rotations of its longitudinal axis.
With reference to figure 19A, improved oscillation bearing structure has and is installed in a 752a through bearing 754a and goes up oscillating deck 751a.This oscillating deck has finger piece 762a and balance mass 764a.The quality of this balance mass body 764a is greater than the quality of the balance mass body 764 of Figure 19 B, and the balance mass body 764a of Figure 19 A with respect to finger piece 762a to be different from the certain angle setting of 180 degree.The result; The vibration that oscillation bearing produced of Figure 19 A can be mated the characteristic that the hammer equipment that comprises this oscillation bearing is in operation more nearly; Therefore, through quality and the position, angle of suitably selecting balance mass body 764a, the vibration that this oscillation bearing produces can minimize.
Those skilled in the art should be understood that the foregoing description only describes with way of example, and has no restrictive meaning, and under the situation that does not break away from the scope of the present invention that is defined by the claims, can carry out variations and modifications.
Claims (9)
1. oscillation bearing structure that is used for power tool; This power tool has housing; Be arranged on the motor in this housing and be suitable for by motor-driven work package, this oscillation bearing structure comprises bonding part and at least one balance mass body; Wherein, Said oscillation bearing structure is suitable for being installed on the axle, makes the rotation of said axle in use cause the reciprocating motion of said bonding part, and at least one said balance mass body is positioned at and deviates from the relative position of diameter, said bonding part.
2. according to the oscillation bearing structure of claim 1, also comprise the circular body part, it is suitable for being installed on the axle, and wherein said bonding part is elongated, and stretches out from said main part.
3. according to the oscillation bearing structure of claim 2, wherein said at least one balance mass body with respect to the bonding part to be different from the certain angle setting of 180 degree.
4. according to the oscillation bearing structure of claim 1, wherein said at least one balance mass body with respect to the bonding part to be different from the certain angle setting of 180 degree.
5. according to any one oscillation bearing structure of claim 1 to 4, wherein said oscillation bearing structure also comprises oscillating deck, and said oscillating deck is suitable for being installed on the axle through bearing.
6. a knocking instrument comprises a kind of oscillation bearing structure according to claim 5, and wherein the quality of balance mass body and position, angle are arranged so that the characteristic that vibration that the oscillation bearing structure is produced can be mated the knocking instrument nearly.
7. according to the knocking instrument of claim 6, said knocking instrument also comprises the hammer piston, and said hammer piston is back and forth driven by the oscillating deck of oscillation bearing structure, and said balance mass body is arranged and hammered into shape piston and does moving of anti-phase.
8. knocking instrument comprises a kind ofly according to any one oscillation bearing structure in the claim 1 to 4, and wherein the quality of balance mass body and position, angle are arranged so that the characteristic that vibration that the oscillation bearing structure is produced can be mated the knocking instrument nearly.
9. according to Claim 8 knocking instrument, said knocking instrument also comprises the hammer piston, and said hammer piston is back and forth driven by the oscillating deck of oscillation bearing structure, and said balance mass body is arranged and is hammered into shape piston and done moving of anti-phase.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB0306525A GB2399615B (en) | 2003-03-21 | 2003-03-21 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
| GB0306525.7 | 2003-03-21 | ||
| GB0323885.4 | 2003-10-11 | ||
| GB0323885A GB0323885D0 (en) | 2003-10-11 | 2003-10-11 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004800076768A Division CN100439045C (en) | 2003-03-21 | 2004-03-19 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101104261A CN101104261A (en) | 2008-01-16 |
| CN101104261B true CN101104261B (en) | 2012-04-18 |
Family
ID=9955241
Family Applications (6)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200710106572 Expired - Fee Related CN101088710B (en) | 2003-03-21 | 2004-03-19 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
| CN 200810171080 Expired - Fee Related CN101422894B (en) | 2003-03-21 | 2004-03-19 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
| CNB2004800076768A Expired - Fee Related CN100439045C (en) | 2003-03-21 | 2004-03-19 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
| CN 200710106573 Pending CN101088711A (en) | 2003-03-21 | 2004-03-19 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
| CN 200710128304 Expired - Fee Related CN101104261B (en) | 2003-03-21 | 2004-03-19 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
| CN 200810171075 Expired - Fee Related CN101422893B (en) | 2003-03-21 | 2004-03-19 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
Family Applications Before (4)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200710106572 Expired - Fee Related CN101088710B (en) | 2003-03-21 | 2004-03-19 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
| CN 200810171080 Expired - Fee Related CN101422894B (en) | 2003-03-21 | 2004-03-19 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
| CNB2004800076768A Expired - Fee Related CN100439045C (en) | 2003-03-21 | 2004-03-19 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
| CN 200710106573 Pending CN101088711A (en) | 2003-03-21 | 2004-03-19 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200810171075 Expired - Fee Related CN101422893B (en) | 2003-03-21 | 2004-03-19 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
Country Status (2)
| Country | Link |
|---|---|
| CN (6) | CN101088710B (en) |
| GB (3) | GB2399615B (en) |
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| DE502005008837D1 (en) * | 2005-11-16 | 2010-02-25 | Metabowerke Gmbh | Motor driven hammer drill |
| JP4756474B2 (en) | 2006-07-20 | 2011-08-24 | 日立工機株式会社 | Electric tool |
| JP5009059B2 (en) * | 2007-06-15 | 2012-08-22 | 株式会社マキタ | Impact tool |
| JP5202997B2 (en) * | 2008-03-05 | 2013-06-05 | 株式会社マキタ | Work tools |
| US8196674B2 (en) * | 2008-03-05 | 2012-06-12 | Makita Corporation | Impact tool |
| DE102008000677A1 (en) * | 2008-03-14 | 2009-09-17 | Robert Bosch Gmbh | Hand tool for impact driven tools |
| JP5345893B2 (en) * | 2009-05-08 | 2013-11-20 | 株式会社マキタ | Impact tool |
| DE102009029055A1 (en) * | 2009-09-01 | 2011-03-10 | Robert Bosch Gmbh | Drilling and / or chiselling device |
| DE102009044938A1 (en) * | 2009-09-24 | 2011-03-31 | Robert Bosch Gmbh | Power tool with a striking mechanism assembly and a balancing mass to compensate for vibrations of the power tool |
| EP2574821B1 (en) * | 2011-09-30 | 2013-10-30 | Siemens Aktiengesellschaft | Active oscillation attenuator without direct acceleration detection |
| CN104209586B (en) * | 2013-05-29 | 2018-02-02 | 博世电动工具（中国）有限公司 | Electric tool |
| CN103273462A (en) * | 2013-06-28 | 2013-09-04 | 李先强 | Electric impactor |
| EP2821183B1 (en) * | 2013-07-05 | 2017-06-21 | Black & Decker Inc. | Hammer Drill |
| CN105537973B (en) * | 2014-10-28 | 2019-03-12 | 黑田精工株式会社 | Table device |
| CN104772101B (en) * | 2015-04-16 | 2016-05-04 | 福州大学 | A kind of oscillation device for Oscillatory Flow Reactor and using method thereof |
| DE18197782T1 (en) * | 2017-09-30 | 2019-07-04 | Positec Power Tools (Suzhou) Co., Ltd | impact tool |
| CN109015847A (en) * | 2018-08-31 | 2018-12-18 | 上海伊斯曼电气股份有限公司 | A kind of vibration at high speed knife |
| CN110216615B (en) * | 2019-06-28 | 2021-02-19 | 国网山东省电力公司济南市章丘区供电公司 | Manual rotary screwdriver |
| CN113441789B (en) * | 2021-07-05 | 2022-10-11 | 浙江皇冠电动工具制造有限公司 | Reciprocating saw |
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- 2003-03-21 GB GB0516659A patent/GB2413612B/en not_active Expired - Fee Related
- 2003-03-21 GB GB0516658A patent/GB2413611B/en not_active Expired - Fee Related
-
2004
- 2004-03-19 CN CN 200710106572 patent/CN101088710B/en not_active Expired - Fee Related
- 2004-03-19 CN CN 200810171080 patent/CN101422894B/en not_active Expired - Fee Related
- 2004-03-19 CN CNB2004800076768A patent/CN100439045C/en not_active Expired - Fee Related
- 2004-03-19 CN CN 200710106573 patent/CN101088711A/en active Pending
- 2004-03-19 CN CN 200710128304 patent/CN101104261B/en not_active Expired - Fee Related
- 2004-03-19 CN CN 200810171075 patent/CN101422893B/en not_active Expired - Fee Related
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| GB2053768A (en) * | 1979-03-28 | 1981-02-11 | Fosroc International Ltd | Percussion apparatus |
| US4991664A (en) * | 1988-08-09 | 1991-02-12 | Kolgan Jury N | Compression-vacuum percussive action machine |
| CN1247494A (en) * | 1996-10-04 | 2000-03-15 | Ina滚动轴承谢夫勒无限责任公司 | Striking tool provided with air-cushion impact mechanism |
Also Published As
| Publication number | Publication date |
|---|---|
| CN101088711A (en) | 2007-12-19 |
| CN100439045C (en) | 2008-12-03 |
| GB2413612B (en) | 2006-01-04 |
| GB2399615B (en) | 2006-03-15 |
| GB0516659D0 (en) | 2005-09-21 |
| GB2413611A (en) | 2005-11-02 |
| CN101088710B (en) | 2013-01-02 |
| CN101422894B (en) | 2011-03-09 |
| CN101422894A (en) | 2009-05-06 |
| GB2399615A (en) | 2004-09-22 |
| GB2413611B (en) | 2006-01-25 |
| GB2413612A (en) | 2005-11-02 |
| CN101422893A (en) | 2009-05-06 |
| GB0516658D0 (en) | 2005-09-21 |
| CN101104261A (en) | 2008-01-16 |
| CN1761553A (en) | 2006-04-19 |
| GB0306525D0 (en) | 2003-04-23 |
| CN101422893B (en) | 2012-05-09 |
| CN101088710A (en) | 2007-12-19 |
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