CN101088710B - 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
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- CN101088710B CN101088710B CN200710106572.8A CN200710106572A CN101088710B CN 101088710 B CN101088710 B CN 101088710B CN 200710106572 A CN200710106572 A CN 200710106572A CN 101088710 B CN101088710 B CN 101088710B
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- mass body
- piston
- gear
- power tool
- hammer
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Images
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
-
- 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
- B25D17/00—Details of, or accessories for, portable power-driven percussive tools
- B25D17/24—Damping the reaction force
- B25D17/245—Damping the reaction force using a fluid
-
- 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
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
-
- 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
- F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
- F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
- F16F15/1201—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon for damping of axial or radial, i.e. non-torsional vibrations
-
- 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
-
- 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
-
- 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
- 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
-
- 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.
Description
Dividing an application of the application for a patent for invention that the application is that application number is 200480007676.8, denomination of invention for " dampening apparatus of power tool and the power tool of this equipment is housed ", the applying date is on March 19th, 2004.
Technical field
The present invention relates to dampening apparatus and the power tool that this equipment is housed for power tool.The present invention in particular but not exclusively relate to for the dampening apparatus of power hammer and the power hammer of 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 is shown in Figure 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 rear handle shell that rear handle 6 and trigger switch device 8 be installed is installed in housing 4,5 rear portion.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, press trigger switch device 8, motor 2 startings are to drive rotatably the armature of this motor.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 the parts that hold within it rigidly.
This motor pinion drives the first gear of intermediate gear device rotatably, and this intermediate 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 the 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 this transmission spindle away from the end of this travelling gear, and this crankshaft cheek is formed be used to the eccentric orfice that holds 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 by 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 by 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 in 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, to form gas-tight seal between this piston 38 and this hollow mandrel 40 inner surfaces.
When motor 2 starting, this armature pinion drives this intermediate gear device rotatably through the first gear, and the second gear of this intermediate gear device drives this transmission spindle rotatably through this travelling gear.This transmission spindle drives this crankshaft cheek 30 rotatably, and the crank arm device that comprises crank-pin 32, crank arm 34 and gudgeon pin 36 will change from the rotary actuation of crankshaft cheek 30 the reciprocal driving to this piston 38 into.By this way, when the user by pressing 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 through narrow groove 9 and filter 11.Therefore, the air pressure in this hammer that changes along with the temperature of this hammer equals the outside air pressure of this hammer.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.
Knownly can reduce vibration to the user's of this power tool impact by absorbing material is set around the 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 dampening apparatus is known, and wherein a plurality of rotatable mass bodies are driven around corresponding rotating shaft, and barycenter and the rotating shaft of these a plurality of rotatable mass bodies are spaced apart, so that these mass bodies produce vibration around the rotation of rotating shaft.Relative phase between speed by controlling these mass bodies and the barycenter of these mass bodies, the vibrational energy that produces 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 not yet are considered to practicable for undesirable vibration that the minimizing power tool produces.
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 the balance mass body that is arranged on the end relative with this finger piece on this axle is partly offset the vibration that this equipment produces.
GB 2256905 discloses a kind of reciprocating-type saw, and wherein the first and second oscillating decks reciprocally drive respectively saw blade and balance mass body, so that the vibration that saw produces is minimum.But the shortcoming of this saw is to arrange a pair of oscillating deck 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, provide a kind of for power hammer equipment dampening apparatus, this power hammer equipment comprises housing, be arranged on the motor in this housing, be suitable for causing that by this motor motion is to realize reciprocating piston in the hole, with the moving mass body that is arranged in this hole, in order to make the described reciprocating motion of described piston in described hole cause that in use described moving mass body is with respect to the reciprocating motion of this housing, impact is passed to the operation element of this hammer equipment, this dampening apparatus comprises at least one drivable mass body, it is suitable for being centered around at least in part at least a portion in this hole, and wherein, at least one described drivable mass body is suitable for being caused to move back and forth by this motor, in order to offset at least in part the vibration of the described housing that is caused with respect to the reciprocating motion of this housing by this moving mass body.
The drivable mass body of at least a portion in this hole is provided at least in part by providing at least one to be suitable for, wherein at least one described drivable mass body makes and is suitable for being caused to move back and forth by this motor, in order to offset at least in part the vibration of the described housing that is caused with respect to the reciprocating motion of this housing by this moving mass body, the advantage that provides like this is to make the structure of power hammer equipment compacter, and reduces to greatest extent simultaneously because the operation of this power hammer equipment imposes on the torque of this housing.
This equipment can also comprise at least one travelling gear, is suitable for by described motor-driven, with the motion that causes described moving mass body and cause at least one described described reciprocating motion that drives mass body.
This vibration absorber also can comprise cam gear, and this cam gear can rotate by at least one travelling gear, and is suitable for engaging at least one described mass body that drives.
This equipment can also comprise the first bias unit, is used at least one described mass body that drives is pushed to described cam gear and engages.
This equipment can also comprise cam follow-up device, is used for changing rotatablely moving of described cam gear at least one described reciprocating motion that drives mass body.
This bias unit can be suitable at least one described mass body that drives is pushed to described 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 described corresponding projection that drives on the mass body.
The advantage that provides like this is to be convenient to this drivable mass body and this cam follow-up device breaks away from.
When power hammer equipment and workpiece broke away from, this drivable mass body or each described drivable mass body can be suitable for mobile the disengaging and the engaging of this cam gear.
This equipment can also comprise holding device, is used for keeping this drivable mass body or each described drivable mass body to break away from described cam gear when power hammer equipment and workpiece disengaging.
This holding device can comprise sealing device, and it is suitable for moving between the operation element of this power hammer equipment and this housing.
This equipment can also comprise disabling device, is used for making described dampening apparatus to lose efficacy.
Described disabling device can comprise be used to the device that described cam gear and described motor are broken away from.
Described disabling device can comprise locking device, is used at least one described drivable mass body in place with respect to this housing locking.
At least one described drivable mass body can be driven by the air that described moving mass body moves.
This equipment can also comprise sensing device, for detection of phase place and/or the amplitude of the vibration that is produced by described dampening apparatus.
This equipment can also comprise adjusting device, is used for regulating phase place and/or the amplitude of the vibration that is produced by described dampening apparatus.
This equipment can also comprise control device, is used for responding the described adjusting device of described sensing devices control.
This equipment can also comprise at least one support member, be used for supporting at least one drivable mass body, and be suitable for being caused to move back and forth by this motor, wherein this at least one described drivable mass body described drive the reciprocating motion of mass body during relatively and at least one described support member be slidably, and this equipment also comprises the second bias unit, engages for described drivable mass body is pushed to at least one described support member.
At least one described support member can comprise sleeve, is used for centering at least in part at least a portion in described hole.
This equipment can also comprise buffer unit, but is used for the impact between at least one drive unit of buffering and at least one the described support member.
According to a further aspect in the invention, provide a kind of power hammer equipment, 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 described motor;
Be arranged on the moving mass body in this hole, it is so that the reciprocating motion of described piston in described hole causes described moving mass body in use with respect to the reciprocating motion of described housing, impact is passed to the operation element of this power hammer equipment; And
Dampening apparatus as defined above.
This equipment can also comprise the piston barrel that limits described hole.
At least one described drivable mass body can be suitable for forming at least a portion of described piston barrel.
The advantage that provides like this is that this power hammer equipment can manufacture more compact structure.
This equipment can also comprise that at least one is arranged on the projection on the described piston barrel, is used for engaging the cam follower means of described dampening apparatus.
At least one described projection can be arranged on the inner surface of described piston barrel.
The advantage that provides like this is the cramped construction that more helps this equipment.
This equipment can also comprise sensor device, for detection of by the vibrative phase place of described dampening apparatus and/or amplitude.
This equipment can also comprise control device, is used for responding described sensor device and controls described adjusting device.
This equipment can also comprise drive unit, is used for making at least one drivable mass body and/or described piston to produce and moves back and forth.
Described drive unit can comprise the axle that is suitable for by described motor rotation, actuator with bonding part, this bonding part is used for describedly driving mass body and/or described moving mass body engages with at least one, and the balance mass body that departs from diameter ground, described bonding part relative position.
According to another aspect of the invention, a kind of dampening apparatus for power tool is provided, this power tool comprises housing, be arranged on the motor in this housing, be suitable for causing the motion of at least one the first operation element of this instrument, this dampening apparatus comprises at least one pair of rotatable mass body, should comprise the corresponding first and second rotatable mass bodies to rotatable mass body or every pair of described rotatable mass body, they are suitable for along mutually opposite direction around the rotation of separately the first and second rotating shafts, wherein, each described first and second gyrating mass body has and the isolated barycenter separately of corresponding described rotating shaft.
At least one described right described first and second mass body can comprise gear separately.
At least one described right described gear can be intermeshing.
At least one described 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 dampening apparatus can also comprise adjusting device, is used for regulating phase place and/or the amplitude of the vibration that is produced by described dampening apparatus.
This equipment can also comprise at least one travelling gear, and it is suitable for by described motor-driven, with the motion that causes at least one described the first operation element and drive described dampening apparatus.
The advantage that provides like this is to guarantee that this vibration absorber is driven with the frequency identical with the first operation element of this instrument.
Described adjusting device can comprise for the device that rotates at least one described travelling gear with respect at least one described first operation element.
Described adjusting device can comprise be used to making at least one described right described mass body relative to each other rotate the device of predetermined angular.
In accordance with a further aspect of the present invention, provide a kind of power tool, comprising:
Housing;
Be arranged on the motor in this housing, it is suitable for causing the motion at least one the first operation element of this instrument; With
Dampening apparatus as defined above.
This motor can be suitable for driving at least one described first operation element through at least one described right described rotatable mass body.
At least one described drivable mass body can be suitable for forming at least a portion of described 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 projection on the described piston barrel, is used for engaging the cam follow-up device of described dampening apparatus.
At least one described projection can be arranged on the inner surface of described piston barrel.
The advantage that provides like this is the further compactness that helps this device structure.
This equipment can also comprise sensor device, for detection of the vibration phase and/or the amplitude that are produced by described dampening apparatus.
This equipment can also comprise control device, is used for responding described sensor device and controls described adjusting device.
This equipment can also comprise drive unit, be used for causing at least one described drivable mass body and/obtain the reciprocating motion of described piston.
This drive unit can comprise the axle that is suitable for by described motor rotation, actuator with the bonding part that is adapted to couple to a few described drivable mass body and/or described moving mass body, and the balance mass body that departs from described bonding part diameter relative position.
In accordance with a further aspect of the present invention, a kind of actuator 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 described bonding part in use, and at least one described balance mass body is positioned at and deviates from the relative position of diameter, described bonding part.
This actuator can also comprise the circular body part that is suitable for being installed on the axle, and wherein, described bonding part is elongated and extends from described main part.
Description of drawings
Below with reference to the accompanying drawings, and only do not have any restriction ground description the preferred embodiments of the present invention by means of example, wherein:
Fig. 1 is the cutaway view of prior art stamping hammer local excision;
Fig. 2 is the dampening apparatus oblique view of first embodiment of the invention;
Fig. 3 is the exploded perspective view of the dampening apparatus of second embodiment of the invention;
Fig. 4 is the oblique view of the dampening apparatus of third embodiment of the invention;
Fig. 5 is the oblique view of the dampening apparatus of fourth embodiment of the invention;
Fig. 6 is the sectional side view of the dampening apparatus of fifth embodiment of the invention;
Fig. 7 is that the dampening apparatus of sixth embodiment of the invention is corresponding to the cutaway view of Fig. 6;
Fig. 8 is that the dampening apparatus of seventh embodiment of the invention is corresponding to the sectional view of Fig. 6;
Fig. 9 is the exploded perspective view of the dampening apparatus of eighth embodiment of the invention;
Figure 10 is the oblique view of the dampening apparatus local excision of ninth embodiment of the invention;
Figure 11 is that the dampening apparatus of tenth embodiment of the invention is corresponding to the partial cutaway view of Figure 10;
Figure 12 is the partial cutaway view of the dampening apparatus of eleventh embodiment of the invention;
Figure 13 A and 13B illustrate dampening apparatus simulated performance shown in Figure 12;
Figure 14 illustrates the data that the simulation of Figure 13 A and 13B draws;
Figure 15 is that the dampening apparatus of twelveth embodiment of the invention is corresponding to the exploded cutaway view of Figure 12;
Figure 16 is that the dampening apparatus of thriteenth embodiment of the invention is corresponding to the exploded cutaway view of Figure 12;
Figure 17 is the section plan of the equipment of Figure 16;
Figure 18 is the dampening apparatus sectional 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 such as the stamping hammer of 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 this gear 102,103 circumference.Pouring weight 106 is so that each gear 102,103 whole barycenter deviate from the rotation through common axis 104.Gear 102,103 helical teeth 105 mutually in the face of and with bevel gear 107 engagements so that wheel 108 rotates along the direction of the arrow A in Figure 2 and causes 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 gear 102,103 pouring weight 106 can be by being realized along the direction rotation bevel gear opposite with arrow C 107 by stepper motor 108.
The below will describe the operation of damper mechanism shown in Figure 2.
Rotatablely moving of each gear 102,103 barycenter can be resolved into barycenter along the sinusoidal motion of a pair of vertical axis perpendicular to the plane of common axis 104 one.Through by 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 dampening apparatus 101 and amplitude can be adjusted to offset at least in part by the hammering that passes to this tool bit by 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 by the cam pin 212 on the gear plate 202.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 makes gear plate 202,203 rotate relative to one another to regulate with respect to the rotation of the angle position mat bevel gear 207 of cam pin 212.
In the embodiment shown in fig. 3, being rotated the vibration that gear 203 produces by the vibration that produces of motion of hammer piston 220 is subdued.Diameter ground is relative haply for pin 212 on pouring weight 206 on gear 203 peripheries and another gear 202.
With reference to figure 4, wherein the parts identical with Fig. 3 embodiment are with identical but increase by 100 Reference numeral and represent, gear 302,303 is installed on the common axis (not shown) and each 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 at its periphery, so that the rotation of its barycenter and gear 303 is spaced apart, and gear 302,303 is respectively driven shaft 310,311 drivings independently of each other, this driving shaft 310,311 has gear 313,314 separately, gear 313,314 respectively with gear 302,305 engagements of 303 tooth.
The hammering action makes moving mass body impacting tube end of body be passed to the drill bit of this instrument by the reciprocating motion of hammer piston.Driving shaft 310 makes cam pin 312 rotations, axle 311 is also driven, so that gear 303 is with the frequency identical with gear 302 but opposite direction rotation, the selection of the phase difference between pouring weight 306 and the cam pin 312 is so that the vibration that the hammering action by this instrument produces is farthest offset in the vibration that is produced by the rotation of gear 303.
With reference to figure 5, wherein the parts identical with Fig. 4 embodiment are with identical but increase by 100 Reference numeral and represent, Fig. 5 discloses a kind of dampening apparatus 401, for the vibration that reduces to be caused by the reciprocating motion of hammering piston 420 into shape, this hammer piston drives again the moving mass body (not shown) for generation of the hammering action.Dampening apparatus 401 is provided with counterweight block 421, and counterweight block 421 is used for doing anti-phase reciprocating motion with hammer piston 420 haply.Hammer piston 420 is connected in crank arm 423 by 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 so that 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, so that pouring weight 406 can be transferred with the relative angular position of counterweight block 421.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 the parts identical with Fig. 5 embodiment are with identical but increase by 1 00 Reference numeral and represent that Fig. 6 shows a kind of compacter dampening apparatus 501, and dampening apparatus 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, 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.
Gear 523 is through meshing by the gear 514 on the driving shaft 511 and the tooth on gear 523 peripheries 532 and rotating around axis 524, and driving shaft 511 causes rotation by the motor (not shown) of this instrument.
This damper mechanism 501 has the cam 533 of installing around gear 523 rigidly, 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 compressed springs 535 on this balance mass body 521 promote to contact with cam 533.The exterior contour of this cam 533 so that cause the rotation of reciprocating gear 534 of hammer piston 520 cause balance mass body 521 with the vibration with respect to piston barrel 530 of the phase place of the reverse movement of hammer piston 520.Because hammer piston 520 and balance mass body 521 are driven by same driving shaft 511, this guarantees that this balance mass body 521 is driven with the frequency identical with this hammer piston 520.Because balance mass body 521 is around this cylindrical shell 530, so this damper mechanism 501 can manufacture compactlyer, and minimized by the torque that the operation of this mechanism produces.
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 is pulled down from workpiece) can make this damper mechanism 501 ineffective, this balance mass body 521 its from the left side farthest position locked in place with respect to cylindrical shell 530, as shown in Figure 6.This is by align to realize that this ball bearing 536 allows these balance mass bodies 521 to slide with respect to piston barrel 530 usually with groove 539 in these balance mass body 521 outer surfaces around the ball bearing 536 of this piston barrel 530 in housing 537.For this balance mass body 521 is in place with respect to these piston barrel 530 lockings when 539 alignment of ball bearing 536 and groove, pin 538 moves to the right side as shown in Figure 6, the result, this ball bearing 536 is moved upwards up to groove 539 on this balance mass body 521 and engages, 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 the parts identical with Fig. 6 embodiment are with identical but increase by 1 00 Reference numeral and represent, sixth embodiment of the present invention damper mechanism 601 has cam 633, it is locked in gear 623 rigidly by means of pin 640 usually, 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 Compress Spring 643 is shifted pin 638 onto the left side, as shown in Figure 7, in order to 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 the parts identical with Fig. 7 embodiment 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 movement 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 movement that balance mass body 721 is substantially anti-phase with hammering piston 720 into shape.
With reference to figure 9, wherein the parts identical with Fig. 7 embodiment 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 by pin 862, and hammer piston 820 is installed on gear 823 by crank arm 831 and cam pin 822.Gear (not shown) on these hammer piston 820 driven shafts drives in the reciprocating motion mode, tooth 832 engagements of the 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 substantially opposite with the motion phase of hammering piston 820 into shape.
Balance mass body 821 is installed on the pin 820 by 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 Compress Spring 841 is pushed down, and ball bearing 842 and the groove 863 of pin 862 are broken away from.This so that pin 862 can be free to slide in the hole 864 of this balance mass body 821.
The damper mechanism 901 of the compactness of ninth embodiment of the invention is shown in Figure 10, and wherein the parts identical with Fig. 9 embodiment 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 engagement.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 by 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.
For this dampening apparatus 901 was lost efficacy, Cam Follower plate 934 moves down as shown in figure 10 in order to 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 the parts identical with Figure 10 embodiment 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 by Compress Spring 1077 and is meshed, and dampening apparatus 1001 overcomes the effect of Compress Spring 1077, loses efficacy by 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 the parts identical with Figure 11 embodiment are with identical but increase by 100 Reference numeral and represent.The hole of cam 1133 through having bearing 1180 is installed on pin 1181, so that the rotation of crank 1182 causes that cam 1133 is around the rotation of rotating shaft 1183.Bearing 1184 is installed on 1121 the pin 1170 of cylindrical shell housing, so that when this cylindrical shell housing 1121 was pushed along arrow D direction, this bearing 1184 contacted with the circumferential surface of cam 1133.Therefore because crank 1182 rotary actuation pistons 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.The movement of piston 1120 in cylindrical shell 1121 causes the movement of tup 1169.Ram 1186 usefulness springs 1187 are installed on the end of cylindrical shell housing 1121, and have the O shape ring 1188 that is installed in the groove 1189, and the ring of the pair of O shape on its end 1,191 1190.
Figure 13 A and 13B illustrate the performance simulation of dampening apparatus shown in Figure 12, and simulation the results are shown in Figure 14.Do not start vibration (16.5 meter per seconds that dampening apparatus produces
2) vibration (6.5 meter per seconds that produce during dampening apparatus with starting
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 the parts identical with Figure 12 embodiment are with identical but increase by 100 Reference numeral and represent.The Cam Follower 1234 that has circular hole 1235 at the one 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.Be installed on the pin 1270 on cylindrical shell 1221 lower surfaces in the hole 1240 of Cam Follower 1234 ends relative with circular port 1235, so that also cause the rotation of cam face 1233 through the rotation of the axle 1238 of arm 1220a driven plunger 1220, the rotation of cam face 1233 causes again the reciprocating motion of hole 1240 and pin 1270.This causes again the linear reciprocal movement of cylindrical shell 1221, and the reciprocating motion of its phase place and piston 1220 is anti-phase.
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, therefore, damper mechanism always opens, and is allowed by the vibration that damper mechanism causes.But the advantage of the embodiment of Figure 15 is to use to greatest extent the structure of existing parts and this equipment of cylinderization, also makes simultaneously the compact conformation of this equipment.
With reference now to Figure 16 and Figure 17,, wherein the parts identical with Figure 15 embodiment 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 is so that this equipment has more compact structure 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 for engaging 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 Cam Follower 1334 pin 1370 by the bias unit (not shown), in order to this dampening apparatus was lost efficacy.When tool bit is pushed to when engaging with workpiece, Cam Follower 1334 is pushed to pin 1370 and engages, so the whole path of pin 1370 by this hole 1340 is received in the notch 1350.
With reference to Figure 18, wherein the parts identical with Fig. 6 embodiment are with identical but increase by 900 Reference numeral and represent that Figure 18 illustrates the dampening apparatus 1401 for power hammer, and this power hammer has the hammer piston 1420 that reciprocatingly slides in piston barrel 1430.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, so that gear 1423 causes that around the rotation of axle 1424 arm 1431 and 1452 is mutually with opposite phase oscillation.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 below will describe the operation of dampening apparatus shown in Figure 180 1401.
When by with tooth 1432 engagements on driving shaft (not shown) and the gear 1423, make gear 1423 when axle 1424 rotation, arm 1431 and 1452 moves along opposite direction mutually.When hammer piston 1420 moves to as shown in figure 18 the left side, 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, until compressed air spring makes ram 1469 move to the left side in mode well-known to those skilled in the art.By this way, hammer piston 1420 moves to the left side of Figure 18 and ram 1469 subsequently slightly has hysteresis between the motion on the left side.
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, Compress Spring 1464 is originally compressed, and then balance mass body 1460 beginnings move right with sleeve 1458.In other words, sleeve 1458 initially moves right, and this sleeve 1458 and balance mass body 1460 move right after lagging behind slightly, with counterweight piston 1420 left initial movable only, then, after lagging behind slightly, hammer piston 1420 and ram 1469 are moved to the left.Be understandable that, by suitably selecting the tensile property of Compress Spring 1464, hysteresis between the motion of sleeve 1458 and balance mass body 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.By the more nearly behavior of coupling hammer piston 1420 and ram 1469, 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 rotation, so that this oscillating deck 751 can be with respect to axle 752 rotations.This oscillating deck 751 has finger piece 755, its arm that is used for engagement piston 720 be arranged to the balance mass body 764 relative with finger piece 762 diameter ground.One skilled in the art will appreciate that when axle 752 during around 754 rotation of its longitudinal axis, cause that finger piece 762 is mobile in complex way along this equipment longitudinal axis, in order to cause the reciprocating motion of hammer piston 720 in piston barrel 730.
With reference to figure 19A, improved oscillation bearing structure has through bearing 754a and is installed in the upper oscillating deck 751a of axle 752a.This oscillating deck has finger piece 762a and balance mass body 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 settings of 180 degree.The result, the vibration that the oscillation bearing of Figure 19 A produces can be mated the feature that the hammer equipment that comprises this oscillation bearing is in operation more nearly, therefore, by 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 above-described embodiment only is described with way of example, and without any restrictive meaning, and in 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 (7)
1. power tool, it comprises:
-housing;
-actuator;
-being arranged on the motor in this housing, described motor connects actuator by driving shaft, and is suitable for making the piston that is in the cylindrical shell produce reciprocating motion by described actuator; And
-be arranged on the damping device on the described housing, described damping device comprise one can driven mass body, the air that the described reciprocating motion that can driven mass body be produced by described piston is moved drives to carry out reciprocating, thereby at least part of payment is done in the vibrations that cause because of the reciprocating motion that described piston carries out with respect to housing.
2. power tool according to claim 1, wherein said can driven mass body be an oscillating deck, and described oscillating deck is installed on the axle through bearing, when axle when the longitudinal axis rotates, this oscillating deck can rotate with respect to axle, to cause the reciprocating motion of described piston in piston barrel.
3. power tool according to claim 2, wherein said oscillating deck has finger piece and balance mass body, described balance mass body with respect to finger piece to be different from the certain angle settings of 180 degree.
4. power tool according to claim 1, wherein at least one describedly can driven mass body be in one through in a passage and the chamber that described cylindrical shell is connected, and wherein the movement of piston in described cylindrical shell causes the air movement in described passage and the described piston barrel.
5. power tool according to claim 4, wherein at least one described anti-phase carrying out of motion that drives mass body and described piston.
6. power tool according to claim 1, wherein said actuator comprises a bonding part and at least one mass body that contends with, wherein said actuator is installed on a rotating shaft, thereby make rotating shaft cause that when rotated described bonding part is reciprocating, wherein at least one described mass body that contends with is in one and leaves the relative position of diameter, described bonding part.
7. power tool according to claim 6, wherein said actuator comprises that also one is installed on the ring bodies in the rotating shaft, wherein said bonding part is slender shape and stretches from described ring bodies.
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB0306525.7 | 2003-03-21 | ||
| GB0306525A GB2399615B (en) | 2003-03-21 | 2003-03-21 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
| 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 |
|---|---|
| CN101088710A CN101088710A (en) | 2007-12-19 |
| CN101088710B true CN101088710B (en) | 2013-01-02 |
Family
ID=9955241
Family Applications (6)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004800076768A Expired - Fee Related CN100439045C (en) | 2003-03-21 | 2004-03-19 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
| CN200710128304.6A Expired - Fee Related CN101104261B (en) | 2003-03-21 | 2004-03-19 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
| CN200810171075.0A Expired - Fee Related CN101422893B (en) | 2003-03-21 | 2004-03-19 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
| CN200810171080.1A Expired - Fee Related CN101422894B (en) | 2003-03-21 | 2004-03-19 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
| CN200710106573.2A Pending CN101088711A (en) | 2003-03-21 | 2004-03-19 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
| CN200710106572.8A Expired - Fee Related CN101088710B (en) | 2003-03-21 | 2004-03-19 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
Family Applications Before (5)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2004800076768A Expired - Fee Related CN100439045C (en) | 2003-03-21 | 2004-03-19 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
| CN200710128304.6A Expired - Fee Related CN101104261B (en) | 2003-03-21 | 2004-03-19 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
| CN200810171075.0A Expired - Fee Related CN101422893B (en) | 2003-03-21 | 2004-03-19 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
| CN200810171080.1A Expired - Fee Related CN101422894B (en) | 2003-03-21 | 2004-03-19 | Vibration reduction apparatus for power tool and power tool incorporating such apparatus |
| CN200710106573.2A Pending CN101088711A (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) | CN100439045C (en) |
| GB (3) | GB2413612B (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 |
| US8196674B2 (en) * | 2008-03-05 | 2012-06-12 | Makita Corporation | Impact tool |
| JP5202997B2 (en) * | 2008-03-05 | 2013-06-05 | 株式会社マキタ | Work tools |
| 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 |
| EP3461593A1 (en) * | 2017-09-30 | 2019-04-03 | Positec Power Tools (Suzhou) Co., Ltd | Percussion 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 |
| CN114571412A (en) * | 2020-12-01 | 2022-06-03 | 博世电动工具（中国）有限公司 | Swing bearing and electric tool |
| 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 GB0306525A patent/GB2399615B/en not_active Expired - Fee Related
-
2004
- 2004-03-19 CN CNB2004800076768A patent/CN100439045C/en not_active Expired - Fee Related
- 2004-03-19 CN CN200710128304.6A patent/CN101104261B/en not_active Expired - Fee Related
- 2004-03-19 CN CN200810171075.0A patent/CN101422893B/en not_active Expired - Fee Related
- 2004-03-19 CN CN200810171080.1A patent/CN101422894B/en not_active Expired - Fee Related
- 2004-03-19 CN CN200710106573.2A patent/CN101088711A/en active Pending
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| GB658284A (en) * | 1947-07-24 | 1951-10-03 | Henry Kielholz | Improvements in or relating to striking hammers with mechanical drive |
| DE2653064A1 (en) * | 1976-11-23 | 1978-05-24 | Gerhard Dipl Ing Vonnemann | Multi impact member rock drill drive - has members crank driven with debris removal system operated by same drive |
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Also Published As
| Publication number | Publication date |
|---|---|
| GB0516659D0 (en) | 2005-09-21 |
| CN101104261A (en) | 2008-01-16 |
| CN101422893A (en) | 2009-05-06 |
| GB2413611A (en) | 2005-11-02 |
| GB2399615B (en) | 2006-03-15 |
| GB2413612A (en) | 2005-11-02 |
| CN100439045C (en) | 2008-12-03 |
| CN101422894B (en) | 2011-03-09 |
| CN101088711A (en) | 2007-12-19 |
| CN101422894A (en) | 2009-05-06 |
| CN101422893B (en) | 2012-05-09 |
| GB0306525D0 (en) | 2003-04-23 |
| CN101088710A (en) | 2007-12-19 |
| GB0516658D0 (en) | 2005-09-21 |
| GB2413612B (en) | 2006-01-04 |
| GB2413611B (en) | 2006-01-25 |
| GB2399615A (en) | 2004-09-22 |
| CN1761553A (en) | 2006-04-19 |
| CN101104261B (en) | 2012-04-18 |
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