CN1915606A - Impact power tool - Google Patents
Impact power tool Download PDFInfo
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- CN1915606A CN1915606A CN 200610111071 CN200610111071A CN1915606A CN 1915606 A CN1915606 A CN 1915606A CN 200610111071 CN200610111071 CN 200610111071 CN 200610111071 A CN200610111071 A CN 200610111071A CN 1915606 A CN1915606 A CN 1915606A
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Abstract
The invention provides a technique of reducing impact force due to the bounceback of a bit after hammering operation in an impact type work tool. The impact type work tool has a tool body, hammer actuating members for executing the hammering operation, drive mechanisms for driving the hammer actuating members and an impact damper for absorbing the impact due to the bounceback after the hammering operation. The impact damper has a weight that receives reaction force transmitted from the hammer actuating members at a reaction force transmitting position where the weight is placed in a state of directly contacting the hammer actuating members or in a state of contacting the hammer actuating members via a hard metal-made intervening member against the reaction force received from the workpiece, and also, an elastic element that is elastically deformed while being pushed with the weight moved backward due to the transmitted reaction force and absorbs the reaction force transmitted to the weight with the elastic deformation.
Description
Technical field
The present invention relates to a kind of impact power tool that machined material is carried out straight line hammering operation, it can relax the reaction force that is subjected to from machined material when the hammering operation.
Background technology
A kind of technology that relaxes the impulsive force that produces owing to the recoil of hitting action back drill bit in hammer drill is disclosed in the flat 8-318342 communique of TOHKEMY.In this hammer drill, between as the axial end of the cylinder of main body side parts and impact bolt, there is elastic tape (buffer unit) as the intermediate member that applies strike to drill bit.And, after the strike of drill bit action, because the reaction force of accepting from this machined material, the drill bit recoil, when impacting bolt bump elastic tape, the deformation by this elastic tape relaxes impulsive force.On the other hand, elastic tape also plays a part the positioning element that when the hammering operation relative machined material is determined the hammer drill body position.Promptly, in the strike action of drill bit, by the user hammer drill main body is applied forwards pressure, the front end of keeping drill bit is pressed in the state (drill bit is remained on hit position) on the machined material, but accepts the pressure of drill bit this moment by elastic tape as the cylinder of main body side parts.
As mentioned above, elastic tape in the past has the function of the impulsive force that mitigation brings by the recoil of drill bit and the positioning function of hammer drill simultaneously when the hammering operation.In order to cushion the recoil of drill bit, preferred soft elastic tape.On the other hand, in order to determine the position of hammer drill better, preferred hard elastic tape.That is, in the structure of elastic tape in the past, require this elastic tape to have different character, it is difficult setting the hardness that can satisfy two functions.
Summary of the invention
Point in view of the above problems the object of the present invention is to provide a kind ofly in impact power tool, helps reducing owing to hit the impulsive force that the recoil of the drill bit after the action brings.
In order to reach above-mentioned problem, according to the present invention, constitute a kind of impact power tool, it has: tool body; The hammering action component, it is configured in the front end area of tool body, simultaneously, the hammering operation of machined material being stipulated by carrying out rectilinear motion at long axis direction; Driving mechanism, it drives the hammering action component with linearity.Impact power tool of the present invention has: weight portion, when it carries out the hammering operation at the hammering action component to machined material, for the reaction force of accepting from machined material, the reaction force of the state definition when being in directly with hammering action component state of contact or being in via the intermediary of hard metal system with hammering action component state of contact transmits the position, and transmission is from the reaction force of hammering action component; Elastic component, it is by strain takes place in the weight portion that rearward moves extruding by reaction force that this transmitted, and absorption is delivered to the reaction force of this weight portion thus.
When carrying out the hammering operation, the hammering action component is accepted reaction force and is recoiled from machined material hitting the action back.According to the present invention, transmit the structure that transmit to weight portion from the hammering action component position by adopting at reaction force, almost 100% reaction force is transmitted.In other words, between hammering action component and weight portion, carry out the transmission of reaction force in the mode of exchange momentum, by the transmission of this reaction force, weight portion to the action direction of reaction force, be that move at the rear.Then, rearward the weight portion of Yi Donging makes the elastic component strain, and this reaction force is absorbed thus.Promptly, according to the present invention, can rearward move and be absorbed in the impulsive force that recoil that the hammering action component produces brings by weight portion, thus, realize the low vibrationization of impact power tool by the strain that moves the elastic component that brings of this weight portion.
In the present invention, it is useful that limiting member is set, and this limiting member limits and makes the elastic force of the elastic component act on weight portion not cross reaction force to transmit the position and act on the place ahead in fact.Thus, can eliminate keeping the otiose power of hammering action component.Consequently, be different from the frequent mechanism as sky is beaten anti-locking mechanism to hammering action component effect bounce forwards, absorb though carry out reaction force, can realize can not producing the reasonability mechanism of the bad influence of elastic force owing to absorbing reaction force.
Further, in the present invention, the preferred setting: the air spring action component, it can switch making the invalid non-operating position of air spring and make between the effective operating position of air spring; Loading component, it should load on non-operating position by action component so that this air spring action component is in the mode of non-operating position.
Description of drawings
Fig. 1 is the integrally-built side sectional view of the electrodynamic type hammer drill that relates to of expression first embodiment of the invention, is the state of expression hammer bit when being crushed on load on the machined material.
Fig. 2 is the amplification view of the main portion of expression hammer drill.
Fig. 3 is the vertical view cutaway drawing that expression has the hammer drill of dynamic shock absorber.
Fig. 4 is the vertical view cutaway drawing of expression hammer bit, is the state of expression hammer bit when being crushed on load on the machined material.
Fig. 5 is the vertical view cutaway drawing of expression hammer drill, the state when being the action of expression buffer.
Fig. 6 is the vertical view cutaway drawing of the electrodynamic type hammer drill that relates to of expression second embodiment of the invention, is the state of expression hammer bit when being crushed on load on the machined material.
Fig. 7 is the vertical view cutaway drawing of the identical hammer drill of expression, the state when being the action of expression buffer.
Fig. 8 is the A portion enlarged drawing of presentation graphs 6.
Fig. 9 is the integrally-built side sectional view of the electrodynamic type hammer drill that relates to of expression third embodiment of the invention, is the state of expression hammer bit when being crushed on load on the machined material.
Figure 10 is the amplification view of the main portion of expression hammer drill.
Figure 11 is the vertical view cutaway drawing of expression hammer drill, is the state of expression hammer bit when not being crushed on non-loaded on the machined material.
Figure 12 is the vertical view cutaway drawing of expression hammer drill, is the state of expression hammer bit when being crushed on load on the machined material.
Figure 13 is the vertical view cutaway drawing of expression hammer drill, the state when being the action of expression buffer.
Figure 14 is the vertical view cutaway drawing of the electrodynamic type hammer drill that relates to of expression four embodiment of the invention, is the state of expression hammer bit when being crushed on load on the machined material.
Figure 15 is the vertical view cutaway drawing of the identical hammer drill of expression, the state when being the action of expression buffer.
Figure 16 is the vertical view cutaway drawing of the electrodynamic type hammer drill that relates to of expression fifth embodiment of the invention, is the state of expression hammer bit when being crushed on load on the machined material.
Figure 17 is the vertical view cutaway drawing of the identical hammer drill of expression, the state when being the action of expression buffer.
The specific embodiment
(first embodiment of the present invention)
Below, at first embodiment of the present invention, be described in detail with reference to Fig. 1～Fig. 5.Present embodiment uses the electrodynamic type hammer drill to describe as an example of impact power tool.Fig. 1 is the integrally-built side view cutaway drawing of the electrodynamic type hammer drill that relates to of expression present embodiment, is the state of expression hammer bit when being crushed on load on the machined material.As shown in Figure 1, as a whole, the agent structure of the hammer drill 101 that present embodiment relates to comprises: form the exterior contour of hammer drill 101 main part 103, via cutter holder 137 loading and unloading freely be installed in the front end area (diagram left side) of this main part 103 hammer bit 119, with the opposition side handle 109 that be connected, that operating personnel hold of the hammer bit 119 of main part 103.Main part 103 is corresponding to " tool body " of the present invention.Hammer bit 119 is keeping at its long axis direction relatively back and forth movement and the state that has been limited with the relative rotation at its circumferencial direction by cutter holder 137.This hammer bit 119 is corresponding to " tool bit " of the present invention.In addition, for convenience of description, before hammer bit 119 sides are called, after handle 109 sides are called.
Main part 103 comprises: held the motor casing 105 of drive motors 111 and held movement conversion mechanism 113, hit the gear-box 107 of member 115 and Poewr transmission mechanism 117.The rotation output of drive motors 111 is delivered on the strike member 115 after suitably being converted to rectilinear motion by movement conversion mechanism 113, hits member 115 via this, produces the impulsive force along long axis direction (left and right directions among Fig. 1) of hammer bit 119.In addition, the rotation of drive motors 111 output is delivered to hammer bit 119 after suitably being decelerated by Poewr transmission mechanism 117, makes this hammer bit 119 be rotated action at circumferencial direction.Handle 109 forms when seeing probably for the コ font from the side, lower end side rotatably is connected the rear end lower of motor casing 105 via rotating shaft 109a at fore-and-aft direction, and the elastomeric spring 109b that upper end side is used via absorption of vibrations is connected to the upper rear end of motor casing 105.Thus, reduce from the transfer of vibration of main part 103 to handle 109.
In Fig. 2, represent main of hammer drill 101 state that has enlarged with cutaway view.The agent structure of movement conversion mechanism 113 comprises: rotated the driven wheel 121 that drives in horizontal plane by drive motors 111, the driven gear 123 that is meshing with each other with this driven wheel 121 and cooperates, the crankshaft cheek 125 that in horizontal plane, rotates integratedly with this driven gear 123, one side's end by the eccentric shaft 126 loosening crank arms 127 that depart from the position of predetermined distance from the pivot of this crankshaft cheek 125 that are connected with embedding shape, be installed in the piston 129 as drive member of the other end of this crank arm 127 by connecting axle 128.Movement conversion mechanism 113 is corresponding to " driving mechanism " of the present invention.Constitute crank mechanism by above-mentioned crankshaft cheek 125, crank arm 127, piston 129.
On the other hand, the agent structure of Poewr transmission mechanism 117 comprises: by drive motors 111 driven driven wheels 121, the transmission gear 131 that cooperates with 121 engagements of this driven wheel, with this transmissions gear 133 in horizontal plane rotating drive shafts 133, be arranged on the bevel pinion 134 of this power transmission shaft 133, be meshing with each other with this bevel pinion 134 and the bevel gear wheel 135 that cooperates, and the cutter holder 137 that in vertical guide, rotates of these 135 whiles of bevel gear wheel.In addition, the structure of hammer drill 101 can suitably be switched and carry out hammer bit 119 is only applied the so-called hammering processing operation that hitting power comes machined material is processed operation along long axis direction, with the hitting power that applies long axis direction with come machined material is processed the so-called hammer drill operation of operation at the revolving force of circumferencial direction, but, this fact and the present invention directly do not concern, its explanation of Therefore, omited.Omit the diagram of machined material for convenience.
Hitting member 115 constitutes for main body with the impact hammer 143 of conduct strike member that piston 129 free slidings ground is configured in the hole inwall of cylinder 141.Impact hammer 143 is driven via the air spring of the air chamber 141a of the cylinder 141 that slides along with the sliding action of piston 129, bump (strike) is delivered to hammer bit 119 via this impact bolt 145 with hitting power being configured on the cutter holder 137 as the impact bolt 145 of intermediate member with being free to slide.Impact bolt 145 and hammer bit 119 corresponding to " hammering action component " of the present invention.In addition, impact bolt 145 is the large-diameter portion 145a by the tube hole inner peripheral surface that closely is entrenched in cutter holder 137 with long axis direction, and and the tube hole inner peripheral surface of cutter holder 137 between have the minor diameter 145b in the space of prescribed level, the tapering 145c formation that forms in the boundary zone of these two 145a of footpath portion, 145b, with large-diameter portion 145a is the front side, and minor diameter 145b is that the mode of rear side is configured in the cutter holder 137.
Hammer drill 101 has location decided part 151, it applies forwards pressing force the user to main part 103, make hammer bit 119 be in the state that is pressed in load on the machined material, contact with the impact bolt 145 of being given as security rearward simultaneously (piston 129 sides) by hammer bit 119, with respect to machined material, the position of decision main part 103.Location decided part 151 be by the elastic tape 153 of the rubber system that forms ring-type and be bonded in this elastic tape 153 axial front face side hard preceding metal washer 155 and be bonded in the assembly of elements that the back metal washer 157 of hard of the axial rearward side of this elastic tape 153 constitutes, be the loosening minor diameter 145b that shape ground is entrenched in impact bolt 145 that embeds.
When location decided part 151 was pressed towards the rear at impact bolt 145, the tapering 145c that impacts bolt 145 contacted with the preceding metal washer 155 of location decided part 151, the leading section of back metal washer 157 contact cylinders 141.Thus, the elastic tape 153 of location decided part 151 is the bounce-back shape and makes and impact bolt 145 and be connected the cylinder 141 that is installed in regularly on the motor casing 107.Elastic tape 153 is corresponding to " elastomeric element " of the present invention.In addition, preceding metal washer 155, its inside diameter forms taper, and when impact bolt 145 was pressed towards the rear, its taper inside diameter closely contacted with the tapering 145c of this impact bolt 145.In addition, back metal washer 157 is by constituting with the tube portion of the chimeric specific length of the minor diameter 145b that impacts bolt 145 and the flange part 145b that stretches out to the external diameter direction from this one, section roughly is hat, and the back of flange part contacts via the axial forward end of spacer 159 with cylinder 141.
The hammer drill 101 that present embodiment relates to has when machined material is carried out the hammering operation, relaxes the buffer 161 of the impulsive force of being brought by the recoil of hitting the hammer bit 119 after moving (reaction force).Buffer 161 is by the long axis direction at drill bit, via preceding metal washer 155 with the tubular weight portion 163 that impacts the hard metal system that bolt 145 contact with always to impacting helical spring 165 formations that bolt 145 sides (the place ahead) load this tubular weight portion 163.Tubular weight portion 163 is corresponding to " weight portion " of the present invention, and helical spring 165 is corresponding to " elastic component " of the present invention, and preceding metal washer 155 is corresponding to " intermediary " of the present invention.
In addition, the hammer drill of present embodiment 101 as represent structure shown in Figure 3 of hammer drill 101 with vertical view cutaway drawing has dynamic shock absorber 171.Dynamic shock absorber 171 is configured in the left and right sides of the long axis that strides across hammer bit 119, about the structure of any one dynamic shock absorber 171 itself all be identical.The agent structure of dynamic shock absorber 171 comprises: in abutting connection with the cylindrical shell 172 that is configured in main part 103, be configured in weight portion 173 in this cylindrical shell 172, be configured in the loading spring 174 of weight portion about 173.Weight portion 173 is corresponding to " constrained vibration weight portion " of the present invention.Loading spring 174 when mobile along the long axis direction (long axis direction of drill bit) of cylindrical shell 172, applies the bounce of subtend in weight portion 173 to weight portion 173.171 pairs of impacts that produce when driving hammer bit 119 of the dynamic shock absorber of Gou Chenging plays the constrained vibration function with periodic vibration as mentioned above.Promptly, during constrained vibration subject that the main part 103 of hammer drill 101 is acted on as the external force (vibration) of regulation, with respect to main part 103, interactive and carry out passive constrained vibration as the weight portion 173 of the constrained vibration member of dynamic shock absorber 171 and loading spring 174 as this constrained vibration subject.Thus, suppress the vibration of the hammer drill 101 of present embodiment effectively.
In addition, the left and right sides of the weight portion 173 in the cylindrical shell 172 of the dynamic shock absorber 171 that present embodiment relates to forms first operating chamber 175 and second operating chamber 176 respectively.First operating chamber 175 is communicated with the crank chamber 177 that always is the closed structure of non-connected state with the outside via the first interconnecting part 175a, second operating chamber 176 is communicated with the cylinder spatial accommodation 178 of gear-box 107 via the second communication chamber 176a, comes down to be communicated with atmosphere.Pressure change in the crank chamber 177 along with the driving of movement conversion mechanism 113.This is based on the rectilinear motion of doing as the piston 129 of the structure member of movement conversion mechanism 113 in cylinder 141.By the variable pressure in this crank chamber 177 is imported first operating chamber 175 from the first interconnecting part 175a, drive the weight portion 173 of dynamic shock absorber 171 energetically, dynamic shock absorber 171 performance constrained vibration effects.That is, dynamic shock absorber 171 actively drives weight portions 173, as shaking and the constrained vibration mechanism of constrained vibration initiatively works, the vibration that produces at main part 103 when more effectively being suppressed at the hammering operation by forcing to add.
Below, the effect of the hammer drill 101 that constitutes is as mentioned above described.When drive motors shown in Figure 1 111 was energized driving, by its rotation output, driven wheel 121 was done spinning movement in horizontal plane.Like this, the driven gear 123 of crankshaft cheek 125 by cooperating with driven wheel 121 engagement, do spinning movement in horizontal plane, thus, by crank arm 127, piston 129 is done linear slide and is moved in cylinder 141.The effect of the air spring in the cylinder 141 of the sliding action by following piston 129, impact hammer 143 is moving linearly cylinder 141 in, and bump (strikes) arrives impact bolt 145, thereby its kinergety is delivered to hammer bit 119.Thus, hammer drill 119 is done the strike action of long axis direction, and machined material is carried out the hammering operation.
When hammer drill 101 was driven in the hammer drill pattern, the driven wheel 121 of rotation was meshing with each other and the transmission gear 131, power transmission shaft 133 and the bevel pinion 134 that cooperate are done spinning movement integratedly in horizontal plane with the rotation output that utilizes drive motors 111.Like this, the bevel gear wheel 135 that cooperates with bevel pinion 134 engagements rotates in vertical guide, and cutter holder 137 and the hammer bit 119 that keeps at this cutter holder 137 rotate integratedly with this bevel gear wheel 135.Like this, when driving by the hammer drill pattern, hammer drill 119 carries out the strike action of long axis direction and the spinning movement of circumferencial direction, and machined material is carried out the hammering operation.
Like this, above-mentioned operation be hammer drill 119 be crushed on the machined material and hammer drill 119 and cutter holder 137 be pressed towards carry out under the state at rear (with reference to Fig. 1～Fig. 4).By rearward being pressed into cutter holder 137, impact bolt 145 and be pressed towards the rear, contact with the preceding metal washer 155 of location decided part 151, simultaneously, back metal washer 157 contacts with the leading section of cylinder 141.That is, the power that is pressed into of hammer drill 119 thus, determines the position of 103 pairs of machined materials of main part by being accepted as the cylinder 141 of main part 103 side components, under this state, carries out hammering operation or hammer drill operation.At this moment, the front end face of the tubular weight portion 163 of aforesaid buffer 161 contacts with the back of the preceding metal washer 155 of location decided part 151.
Then, after 119 pairs of machined materials of hammer bit hit action,, produce recoil strength at this hammer bit 119 owing to reaction force from machined material.By this recoil strength, the rearward reaction force of impact bolt 145 effects.At this moment, the tubular weight portion 163 of buffer 161 is by the preceding metal washer 155 contact impact bolts 145 of location decided part 151.Thus, the reaction force of impact bolt 145 is delivered to tubular weight portion 163 by the contact condition with this preceding metal washer 155.In other words, between impact bolt 145 and tubular weight portion 163, carry out momentum-exchange.By the transmission of such reaction force, impact bolt 145 and be in almost static state at hit position, on the other hand, tubular weight portion 163 is to moving as the action direction rear of reaction force.Then, the reaction force of the tubular weight portion 163 that rearward moves is absorbed helical spring 165 generation strains by this tubular weight portion 163.This state as shown in Figure 5.
At this moment, the reaction force that impacts bolt 145 also act on certainly be in phase impact bolt 145 via preceding metal washer 155 elastic tape 153 of state of contact.But the transmission of power is corresponding with the Young's modulus of the object that is in contact condition, and transport also uprises.According to present embodiment, the tubular weight portion 163 of buffer 161 is the metallic article of hard, Young's modulus height (greatly).On the other hand, elastic tape 153 is a rubber, and Young's modulus is low.Thus, the major part of impacting the reaction force of bolt 145 is delivered to metal impact bolt 145 via the preceding metal washer 155 of hard and is in contact condition, the tubular weight portion 163 that Young's modulus is high.Like this, be created in the impulsive force that produces by recoil on hammer bit 119 and the impact bolt 145, move and make helical spring 165 that strains take place by tubular weight portion 163 is rearward by moving of this tubular weight portion 163, can be absorbed effectively, thus the low vibrationization of realization hammer drill 101.
Like this, according to present embodiment, after hitting action, hammer bit 119 and impact that bolt 145 accepts from the machined material reaction force, its major part is passed to tubular weight portion 163 from this impact bolt 145, therefore, is in roughly inactive state from this impact bolt 145 of hit position.Thus, the reaction force that acts on the elastic tape 153 diminishes, and the elastic deformation amount of the elastic tape 153 that is produced by this reaction force becomes very little, also reduces counter the having an effect after it.In addition, the buffer 161 that is made of tubular weight portion 163 and helical spring 165 result that can absorb the reaction force that impacts bolt 145 can form hard elastic tape 153.Consequently by this elastic tape 153 can 103 pairs of machined materials of realization body portion the rationalization of determining positions.
In addition, in the present embodiment, by the loading force of stopper 169 restriction helical springs 165, the loading force of restriction helical spring 165 makes it not cross hit position and acts on the place ahead in fact.Thus, in hitting action, at the pressing force that main part 103 is applied forwards, with hammer bit 119 and when impacting bolt 145 and remaining on hit position, possess the helical spring 165 that is used to absorb reaction force, can prevent simultaneously keeping this hammer bit 119 and impacting the generation of bolt 145 otiose power.Therefore, be different from as empty beat the anti-locking mechanism in hitting operation always to hammer bit 119 and impact the mechanism that bolt 145 acts on bounce forwards, reaction force can be absorbed, but the dysgenic reasonability of elastic force mechanism can be do not produced fully owing to the absorption of reaction force.
In addition, according to present embodiment, the mechanicalness restriction is carried out in the position in the place ahead by 169 pairs of tubular weight of stopper portion 163, again by making the loading force that is produced by helical spring 165 act on tubular weight portion 163, can limit this tubular weight portion 163 and cross hit position and move.Thus, the become setting etc. of weight of the setting of the loading force that is easy to carry out helical spring 165 or tubular weight portion 163 is used to absorb the condition enactment of reaction force.
In addition, according to present embodiment, from the reaction force of machined material via hammer bit 119 and impact bolt 145 and be delivered to tubular weight portion 163.Thus, can on the way not disperse, and can be delivered to tubular weight portion 163 in the concentrated area from the reaction force of machined material.Therefore, can improve efficient from reaction force to tubular weight portion 163 that transmit, improve the bump absorption function.
In addition, in the present embodiment, tubular weight portion 163 and location decided part 151 on the major axis that radially is configured in hammer bit 119 side by side same position and constitute.Thus, can be implemented on the basis of seeking to save spatialization and can realize the reasonable configuration structure.In addition, tubular weight portion 163 carries out with the preceding metal washer 155 that is connected via shared horminess metal plate that impacts bolt 145 with elastic tape 153.Therefore,, the reaction force that impacts bolt 145 is transmitted via tubular weight portion 163 and 153 liang of paths of elastic tape from a place of this impact bolt 145 by common preceding metal washer 155, simultaneously, but simplified structure.
(second embodiment of the present invention)
Below, at second embodiment of the present invention, describe with reference to Fig. 6～Fig. 8.This embodiment is to constitute in the mode that the reaction force (recoil) that will hit when action from hammer bit 119 is delivered to buffer 161, removes this structure, and is identical with the structure of above-mentioned first embodiment.Therefore, in illustrated each parts,, use identical mark, omit or simply its explanation for having the structure member identical with first embodiment.In this embodiment, the axial central portion that impacts bolt 145 is large-diameter portion 145a, has minor diameter 145b, 145d respectively in rear side and the front side of this large-diameter portion 145a.In addition, form tapering 145c at the minor diameter 145b of rear side and the boundary portion of large-diameter portion 145a, the preceding metal washer 155 of location decided part 151 contacts with this tapering 145c via the conical surface.On the other hand, the external diameter that impacts the minor diameter 145d of bolt 145 front sides is set forr a short time than the external diameter of hammer bit 119.In addition, between the inner peripheral surface of outer peripheral face that impacts bolt 145 and cutter holder 137, be set with the big space of regulation.
On the other hand, the tubular weight portion 163 as the structure member of buffer 161 that is made of hard metal is configured between the tube hole inner peripheral surface of the zone, periphery front side of the outer peripheral face of location decided part 151 and cylinder 141 and cutter holder 137, with the inner peripheral surface state of contact of this cutter holder 137 under, can move along the long axis direction of drill bit.Tubular weight portion 163 is corresponding to " weight portion " of the present invention.In addition, it is littler than the diameter of posterior region that tubular weight portion 163 forms axial zone, front side, simultaneously, this small diameter portion by cutter holder 137 inner peripheral surface and the space of impacting between the outer peripheral face of bolt 145 forwards extend.Then, the large-diameter portion 145a that impacts bolt 145 in axially can being entrenched in the tube hole of the minor diameter extension 163a that forwards extends with relatively moving, further, be provided with the flange shape contact site 163b that the minor diameter 145d towards the front side of impacting bolt 145 stretches out to internal side diameter in the front zone of the tube hole of minor diameter extension 163a inner peripheral surface.Given as security under the rearward load condition at hammer bit 119, the front of this contact site 163b contacts with surface contact state with the head circumference 119a (rearward end) of hammer bit 119 by the conical surface.Thus, after the strike action of hammer bit 119, when these hammer bit 119 acceptance recoiled from the machined material reaction force, the reaction force of hammer bit 119 was passed to the tubular weight portion 163 that is in direct contact condition with hammer bit 119.
In addition, its inner peripheral surface that stretches out the end of the conduct of contact site 163b closely is entrenched in the periphery of the minor diameter 145d of the front side of impacting bolt 145.Thus, impact the large-diameter portion 145a of bolt 145 and two places of minor diameter 145d of front side and supported, with the stabilisation that realizes axially relatively moving and moving by tubular weight portion 163.In addition, between the back of the end difference 163c of the minor diameter extension 163a of the front of the preceding metal washer 155 of location decided part 151 and tubular weight portion 163, be set with and allow this tubular weight portion 163 because the gap of the necessary size that rearward moves from the reaction force of hammer bit 119.
Constitute the hammer drill 101 that present embodiment relates to as mentioned above.Therefore, under hammer bit 119 was crushed on load condition on the machined material, because hammer bit 119 and impact bolt 145 and be pressed towards the rear, the head of this hammer bit 119 contacted with the contact site 163b of tubular weight portion 163.In addition, when the tapering 145c of impact bolt 145 contacted with the preceding metal washer 155 of location decided part 151, back metal washer 157 contacted with the leading section of cylinder 141.Like this, the power that is pressed into of hammer bit 119 is by being accepted as the cylinder 141 of main part 103 side components.This state is Fig. 6～shown in Figure 8.
Under this state, when carrying out the strike action of hammer bit 119, hit the action back owing to reaction force, and produce recoil strength at this hammer bit 119 from machined material.The reaction force of hammer bit 119 is passed to the tubular weight portion 163 that is in this hammer bit 119 contact conditions.Thus, tubular weight portion 163 moves to the rear as the action direction of reaction force, makes helical spring 165 that strains take place.Like this, the impulsive force that is produced by the recoil of hammer bit 119 is cushioned device 161 and absorbs, thereby realizes the low vibrationization of hammer drill 101.This state as shown in Figure 7.
According to present embodiment, to be delivered to tubular weight portion 163 from being positioned at the hammer bit 119 that impacts bolt 145 the place aheads from the reaction force of machined material, therefore, be easy to guarantee to be configured in the broad space that is used to dispose tubular weight portion 163 of rear area of hammer bit 119 of the front end area of main part 103, the free degree when improving the weight of design tubular weight portion 163 or axial length etc.
In addition, above-mentioned embodiment is that example is illustrated with hammer drill 101 as impact power tool, still, is not limited to hammer drill 101, certainly is applicable to hammer.In addition, in the above-mentioned embodiment, about bang path, for being delivered to the mode of tubular weight portion 163 from impacting bolt 145 to the reaction force of tubular weight portion 163, with be delivered to the mode of tubular weight portion 163 from hammer bit 119, but can form the structure that possesses these two modes respectively.That is, also can a plurality of tubular weight portion be set, will be delivered to a side tubular weight portion, will be delivered to the opposing party's tubular weight portion from the reaction force of drill bit from the reaction force that impacts bolt at main part 103.In addition, also can be shape beyond the tubular as the tubular weight portion 163 of the structure member of buffer 161.In addition,, also can change dynamic shock absorber 171, use counterweight as moving the constrained vibration mechanism of constrained vibration by straight line with hammer bit 119 is equidirectional.
In addition, in the above-described embodiment, illustrated for linearity ground driving hammer bit 119, use crank mechanism to be converted to straight-line movement conversion mechanism 113 as rotation output with drive motors 111, but,, be not limited to crank mechanism as movement conversion mechanism, for example, can utilize at the swash plate that axially carries out swing movement (swash plate) to come as the motion transformational structure.In addition, in the above-described embodiment, forbid that by stopper 169 tubular weight portion 163 forwards moves, the loading force of restriction helical spring 165, the loading force that limits this helical spring 165 is crossed impact position and is acted on the place ahead in fact, limits but also can change by stopper 169, for example, also can change into and not load initial stage load, with the structure of free state configuration helical spring 165.
(the 3rd embodiment of the present invention)
Below, at third embodiment of the invention, be elaborated with reference to Fig. 9～Figure 13.This embodiment is further to have added empty structure of beating anti-locking mechanism, removes this structure, and is identical with the structure of above-mentioned first embodiment.Therefore, in illustrated each parts,, use identical mark, omit or simply its explanation for having the structure member identical with first embodiment.
The hammer drill 101 of present embodiment possesses sky and beats anti-locking mechanism 181, and it is not pressed towards under the no-load condition at rear at hammer bit 119, forbids that drive motors 111 is energized the strike action of this hammer bit 119 when driving.Effect by air spring drives the air chamber 141a of impact hammer 143 by spiracle 141b and external communications.Empty beat anti-locking mechanism 181 and exist as the mechanism of the switch of controlling this spiracle 141b.Empty agent structure of beating anti-locking mechanism 181 comprises: in the release position of open spiracle 141b and close between the closed position of spiracle 141b carry out the action sleeve 183 of change action, in order to make action sleeve 183 be in the release position of open spiracle 141b and will to move the pressing spring 185 of sleeve 183 to the release position loading.The release position is corresponding to " non-operating position " of the present invention, and the closed position is corresponding to " operating position " of the present invention.In addition, action sleeve 183 is corresponding to " air spring action component " of the present invention, and pressing spring 185 is corresponding to " loading component " of the present invention.
In addition, in the present embodiment, illustrated is the form that constitutes axially being split into 2 sleeves of action sleeve 183, but these two sleeves also each other one move, also can be essentially parts.In addition, the tube portion diameter of the rear portion packing ring 157 of the diameter of action sleeve 183 and location decided part 151 is formed about equally.Therefore, because the tube portion of action sleeve 183 and rear portion packing ring 157 interferes mutually, in the present embodiment, in the tube portion of action sleeve 183 and rear portion packing ring 157, set the mutually different joint-cutting of shape at circumferencial direction, avoid mutual interference thus, simultaneously, configurable on same diameter.
Below, describe at the effect of the hammer drill 101 that constitutes as mentioned above.Showing in Figure 11 does not have pressing force to act on no-load condition on the main part 103.Under this no-load condition, by the effect that sky is beaten the loading spring 185 of anti-locking mechanism 181, action sleeve 183 is pressed towards the place ahead and is in the release position that makes spiracle 141b open.Under this state, air chamber 141a is communicated with outside by spiracle 141b, and the air spring effect becomes invalid.In addition, be loaded the action sleeve 183 of 185 doses of pressures of spring, the internal diameter flange part 183a of its front end contacts with the back of the 157b of medial flange portion of the rear portion packing ring 157 of location decided part 151, remains on the release position.
On the other hand, if by the user main part is applied forwards pressing force, hammer bit 119 is crushed on the machined material, then impacts bolt 145 and be pressed towards piston 129 sides at rear with the hammer bit 119 that is rebounded on this machined material.The internal diameter flange part 183a of the tapering 145f contact action sleeve 183 of the rear side of the impact bolt 145 that has rearward moved, simultaneously, the loading force of opposing loading spring 185 makes this action sleeve 183 rearward mobile.Thus, action sleeve 183 is closed the spiracle 141b of air chamber 141a, and it is effective that the effect of air spring becomes.In addition, impact the preceding metal washer 155 of bolt 145 by the tapering 145c contact position decision parts 151 of front side.Like this, act on the cylinder 141 that pressing force on the hammer bit 119 is used as main part 103 side components and accept, determine the position of 103 pairs of machined materials of main part thus.In addition, its front end face of the tubular weight portion 163 of aforesaid buffer 161 contacts with the back of the preceding metal washer 155 of location decided part 151.This load condition as shown in figure 12.
Drive motors 111 is energized when driving, and utilizes its rotation output, and driven wheel 121 is done spinning movement in horizontal plane.Like this, crankshaft cheek 125 is by doing spinning movement with driven wheel 121 driven gear 123 that cooperates that is meshing with each other in horizontal plane, and thus, by crank arm 127, cylinder 129 is done the linear slide action in cylinder 141.At this moment, if action sleeve 183 is in the no load condition of open spiracle 141b in the release position, then the air of this air chamber 141a is emitted or is sucked to the outside by spiracle 141b, thereby the compression spring is not had an effect to air chamber 141a.That is, prevent hammer bit 119 empty beating.On the other hand, be in the load condition of the closed position of closing spiracle 141b at action sleeve 183, under the effect of the air spring of the air chamber 141a of the sliding action of following piston 129, make collision device 143 in cylinder 141, do rectilinear motion and collide (strike) impact bolt 145, its kinetic energy is delivered to hammer bit 119.Thus, hammer bit 119 is done the strike action of long axis direction, and machined material is carried out the hammering operation.
When carrying out above-mentioned hammering operation or hammer drill operation, after 119 pairs of machined materials of hammer bit hit action, because the reaction force from machined material produces recoil strength on this hammer bit 119, then by these recoil strength impact bolt 145 effects reaction force backward.The reaction force of impact bolt 145 is passed to tubular weight portion 163 by the contact condition of this preceding metal washer 155, simultaneously, makes helical spring 165 that strains take place by this tubular weight portion 163 and is absorbed.This state as shown in figure 13.
(four embodiment of the invention)
Below, at four embodiment of the invention, be elaborated with reference to Figure 14 and Figure 15.This embodiment is that the reaction force (recoil strength) when hitting action is delivered to buffer 161 and constitutes from hammer bit 119, identical about this structure with the second above-mentioned embodiment, in addition, beat anti-locking mechanism 181 about sky, identical with the structure of above-mentioned the 3rd embodiment.Therefore, in illustrated each parts,, use identical mark, omit or simply its explanation for having the structure member identical with above-mentioned embodiment.
In the hammer drill 101 that present embodiment relates to, under hammer bit 119 is crushed on load condition on the rapidoprint, because hammer bit 119 and impact bolt 145 and be pressed towards the rear makes the contact site 163b of the head contact tubular weight portion 163 of this hammer bit 119.In addition, when impacting the preceding metal washer 155 of tapering 145c contact position decision parts 151 of bolt 145, rear portion packing ring 157 contacts with the leading section of cylinder 141.Like this, the power that is pressed into of hammer bit 119 cylinder 141 that is used as main part 103 side components is accepted.On the other hand, rearward be pressed into by impacting bolt 145, the tapering 145f of these impact bolt 145 rear sides is contacted with the internal diameter flange part 183a of action sleeve 183, simultaneously, the active force of opposing loading spring 185 rearward moves this action sleeve 183.Thus, action sleeve 183 is closed the spiracle 141b of air chamber 141a, and it is effective that the effect of air spring becomes.This state as shown in figure 14.
Under this state, be energized driving at drive motors 111, when carrying out the strike action of hammer bit 119,, on this hammer bit 119, produce recoil strength hitting the action back owing to reaction force from machined material.The reaction force of hammer bit 119 is passed to the tubular weight portion 163 that is in this hammer bit 119 contact conditions.Thus, tubular weight portion 163 moves to the rear as the action direction of reaction force, makes helical spring 165 produce strains.Like this, the impulsive force that produces owing to the recoil strength of hammer bit 119 is cushioned device 161 and absorbs, thereby realizes the low vibrationization of hammer drill 101.This state as shown in figure 15.
(the 5th embodiment of the present invention)
Below, at fifth embodiment of the invention, be elaborated with reference to Figure 16 and Figure 17.This embodiment is to have omitted the elastic tape 155 of the location decided part 151 that has illustrated in above-mentioned the 3rd embodiment and constitute, and removes outside this point, comprises emptyly beating anti-locking mechanism 181 all the structure with the 3rd embodiment being identical.Therefore, in illustrated each parts,, use identical mark, omit or simply its explanation for having the structure member identical with the 3rd embodiment.In this embodiment, location decided part 151 only is made of metal washer 155.This positioning metal washer 155, the internal diameter end difference 137a of its front and cutter holder 137 is in contact condition, and the back side is stopped 191 on ring and stops.That is, metal washer 155 is mounted to forbid the state that cutter holder 137 moves along the drill bit long axis direction, when impacting bolt 145 and be pressed towards the load at rear with hammer bit 119, as shown in figure 16, contacts with the tapering 145c of these impact bolt 145 front sides.
According to the 5th embodiment, be crushed on load condition on the machined material at hammer bit 119, by hammer bit 119 and impact bolt 145 and be pressed towards the rear, impact the tapering 145c contacting metal packing ring 155 of the front side of bolt 145.Because metal washer 155 is fixed on the cutter holder 137, accepts so the pressing force of hammer bit 119 is used as the cutter holder 137 of main part 103 side components.On the other hand, owing to impact bolt 145 rearward being pressed into, the tapering 145f of these impact bolt 145 rear sides is contacted with the internal diameter flange part 183a of action sleeve 183, simultaneously, the active force of opposing loading spring 185 rearward moves this action sleeve 183.Thus, action sleeve 183 is closed the spiracle 141b of air chamber 141a, and it is effective that the effect of air spring becomes.This state as shown in figure 16.
Under this state, be energized driving at drive motors 111, when carrying out the strike action of hammer bit 119,, on this hammer bit 119, produce recoil strength hitting the action back owing to reaction force from machined material.By this recoil strength, rearward reaction force acts is being impacted on the bolt 145.At this moment, because the tubular weight portion 163 of buffer 161 contacts with impact bolt 145 by metal washer 155, make the reaction force that impacts bolt 145 be passed to the tubular weight portion 163 that is in via the contact condition of metal washer 155, this tubular weight portion 163 rearward moves.Then, the reaction force of the tubular weight portion 163 that rearward moves is absorbed helical spring 165 generation strains by this tubular weight portion 163.This state as shown in figure 17.
At this moment, owing to, also might act on cutter holder 137 via metal washer 155 so impact the reaction force of bolt 145 by stopping to encircle 191 restriction metal washers 155 moving axially on cutter holder 137.But, for metal washer 155 with stop to encircle 191 contact, there is no need to be set at compact state, can allow to have a little gap.On the other hand, the contact condition of 163 pairs of metal washers 155 of tubular weight portion be in helical spring 165 elastic force effects state under contact, can keep state fully closely.Therefore, the major part of the reaction force of impact bolt 145 is passed to the tubular weight portion 163 that is in tight connection status with metal washer 155.Like this, move by the rearward of tubular weight portion 163, with the impulsive force that the recoil that makes helical spring 165 strains can be absorbed in hammer bit 119 and 145 generations of impact bolt effectively by moving of this tubular weight portion 163 generates, realize the low vibrationization of hammer drill 101.That is,, under the situation that does not have elastic tape 153 structures, can reasonably absorb and hit the impulsive force that the action back produces owing to the recoil of hammer bit 119 according to present embodiment.
In addition, any one above-mentioned embodiment all is to be the explanation that example is carried out with hammer drill 101 as impact power tool, still, is not limited to hammer drill 101, certainly is applicable to hammer.And if hammer bit 119 only hits operation, then about making the location decided part 151 of the power that is pressed into of accepting hammer bit 119, the fixed object fixing as being used for not moving axially also can be shell.In addition, in the above-mentioned embodiment, about bang path, for being delivered to the mode of tubular weight portion 163 from impacting bolt 145 to the reaction force of tubular weight portion 163, with be delivered to the mode of tubular weight portion 163 from hammer bit 119, but can form the structure that possesses these two modes respectively.That is, also can a plurality of tubular weight portion be set, will be delivered to a side tubular weight portion, will be delivered to the opposing party's tubular weight portion from the reaction force of drill bit from the reaction force that impacts bolt at main part 103.In addition, also can be shape beyond the tubular as the tubular weight portion 163 of the structure member of buffer 161.In addition, by moving the dynamic damper that carries out main part 103 constrained vibrations at the equidirectional straight line of doing, also can and use with constrained vibration mechanism such as counterweight with hammer bit 119.
In addition, in the above-described embodiment, illustrated for linear drives hammer bit 119, use crank mechanism to be converted to straight-line movement conversion mechanism 113 as rotation output with drive motors 111, but,, be not limited to crank mechanism as movement conversion mechanism, for example, can utilize at the swash plate that axially carries out swing movement (swash plate) to come as the motion transformational structure.
In addition, it is the structures (mode arranged side by side) that are independent of buffer 161 that sky in the above-mentioned embodiment is beaten anti-locking mechanism 181, based on shift action at the fore-and-aft direction that impacts bolt 145, release position at open spiracle 141b, and close the structure that moves between the closed position of spiracle 141b, but also can adopt the structure of carrying out shift action by buffer 161.Promptly, also can be by hammer bit 119 by being pressed on the machined material, when impact bolt 145 is pressed into main part 103 sides with this hammer bit 119, the tubular weight portion 163 of buffer 161 is impacted bolt 145 extruding and is carried out backward movement, accompany with it, by helical spring 165, the empty action sleeve of beating in the anti-locking mechanism 181 183 of extruding, do backward movement to the closed position of closing spiracle 141b, then, tubular weight portion 163 is in the position of having carried out backward movement, carries out the action of the reaction force when absorbing the strike action of hammer bit 119.In other words, the buffer that is in user mode is done backward movement simultaneously with impacting bolt 145, keeps the bounce of helical spring 165, makes the empty action sleeve 183 of beating anti-locking mechanism 181 move effective operating position to air spring simultaneously and moves.
In addition, in the present embodiment, beat arranged side by side use of anti-locking mechanism 181 both sides with buffer 161 and sky and be illustrated, but also can make action sleeve 183 be used for the tubular weight portion 163 of buffer 161 by suitably adjusting empty weight of playing the action sleeve 183 of anti-locking mechanism 181 to example.
Claims (12)
1. impact power tool is characterized in that having:
Tool body;
The hammering action component, it is configured in the front end area of above-mentioned tool body, simultaneously, the hammering operation of machined material being stipulated by carrying out rectilinear motion at long axis direction;
Driving mechanism, it is by air spring, the above-mentioned hammering action component of linearly driving;
Weight portion, when it carries out the hammering operation at above-mentioned hammering action component to above-mentioned machined material, for the reaction force of accepting from this machined material, transmitting the position according to being in directly with above-mentioned hammering action component state of contact or being in the reaction force that intermediary and above-mentioned hammering action component state of contact via hard metal system be defined, transmission is from the above-mentioned reaction force of above-mentioned hammering action component;
Elastic component, above-mentioned weight portion's extruding that it based on the reaction force that is transmitted and is rearward moved and strain takes place absorbs the reaction force that is passed to this weight portion thus;
Limiting member, it limits and makes the elastic force of the above-mentioned elastic component act on above-mentioned weight portion not cross above-mentioned reaction force to transmit the position and act on the place ahead.
2. the impact power tool of putting down in writing as claim 1 is characterized in that,
Have elastomeric element, it is different parts with above-mentioned elastic component, between above-mentioned hammering action component and above-mentioned tool body, be the bounce-back shape above-mentioned hammering action component is connected in above-mentioned tool body,
When carrying out the hammering operation, when above-mentioned hammering action component was pressed on above-mentioned machined material, the power that is pressed into that acts on this hammering action component was accepted by above-mentioned tool body by above-mentioned elastomeric element.
3. the impact power tool of putting down in writing as claim 2 is characterized in that, above-mentioned weight portion and the same position of above-mentioned elastomeric element on the major axis of above-mentioned hammering action component are to be configured in the mode that radially is shape arranged side by side.
4. as claim 2 or 3 impact power tools of being put down in writing, it is characterized in that, above-mentioned hammering action component and contacting of above-mentioned weight portion and above-mentioned elastomeric element be by between above-mentioned hammering action component and above-mentioned weight portion and the reaction force transferring elements of the shared hard metal system between above-mentioned hammering action component and the above-mentioned elastomeric element carry out.
5. as any impact power tool of being put down in writing in the claim 1 to 4, it is characterized in that,
Above-mentioned limiting member is not transmit the mode that forwards moves the position and prevent the stopper of the action of above-mentioned weight portion to constitute by not crossing above-mentioned reaction force by contacting with above-mentioned weight portion with this weight portion.
6. as any impact power tool of being put down in writing in the claim 1 to 5, it is characterized in that,
Above-mentioned hammering action component has the impact bolt of accepting the driving force that above-mentioned driving mechanism produces and the bump by this impact bolt carries out straight-line tool bit,
Above-mentioned impact bolt by with the contact condition of above-mentioned weight portion, and will be delivered to this weight portion from the reaction force of above-mentioned machined material.
7. as any impact power tool of being put down in writing in the claim 1 to 5, it is characterized in that,
Above-mentioned hammering action component has the impact bolt of accepting the driving force that above-mentioned driving mechanism produces and the bump by this impact bolt carries out straight-line tool bit,
Above-mentioned tool bit by with the contact condition of above-mentioned weight portion, and will be delivered to this weight portion from the reaction force of above-mentioned machined material.
8. as any impact power tool of being put down in writing in the claim 1 to 7, it is characterized in that,
Be provided with constrained vibration weight portion, this constrained vibration weight portion is different parts with above-mentioned weight portion, and it is connected with above-mentioned tool body, simultaneously, and by towards linearly the moving of the direction identical and constrained vibration with above-mentioned hammering action component.
9. as any impact power tool of being put down in writing in the claim 1 to 8, it is characterized in that having:
The air spring action component, it can switch making the invalid non-operating position of above-mentioned air spring and make between the effective operating position of above-mentioned air spring,
Loading component, it is so that above-mentioned air spring action component is in the mode of above-mentioned non-operating position that this action component is loaded towards non-operating position.
10. the impact power tool of putting down in writing as claim 9, it is characterized in that, above-mentioned air spring action component is when the hammering operation, when being pressed in above-mentioned hammering action component on the above-mentioned machined material, directly pushed, move to above-mentioned operating position from above-mentioned non-operating position by the hammering action component that rearward moves by this machined material extruding.
11. as any impact power tool of being put down in writing in the claim 1 to 10, it is characterized in that, above-mentioned intermediary between above-mentioned hammering action component and above-mentioned weight portion is installed in above-mentioned tool body in the mode that does not move along the long axis direction of above-mentioned hammering action component.
12. an impact power tool is characterized in that having:
Tool body;
The hammering action component, it is configured in the front end area of above-mentioned tool body, simultaneously, the hammering operation of machined material being stipulated by carrying out rectilinear motion at long axis direction;
Driving mechanism, it passes through air spring and the above-mentioned hammering action component of linearly driving;
Weight portion, when it carries out the hammering operation at above-mentioned hammering action component to above-mentioned machined material, for the reaction force of accepting from this machined material, reaction force when being in directly with above-mentioned hammering action component state of contact or being in intermediary via hard metal system with above-mentioned hammering action component state of contact transmits the position, and transmission is from the above-mentioned reaction force of above-mentioned hammering action component;
Elastic component, its absorption are passed to the reaction force of above-mentioned weight portion;
The air spring action component, it can switch making the invalid non-operating position of above-mentioned air spring and make between the effective operating position of above-mentioned air spring;
Loading component, it is so that above-mentioned air spring action component is in the mode of above-mentioned non-operating position that this action component is loaded towards non-operating position.
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005-239118 | 2005-08-19 | ||
| JP2005239118A JP4509890B2 (en) | 2005-08-19 | 2005-08-19 | Impact type work tool |
| JP2005239118 | 2005-08-19 | ||
| JP2005247679A JP4509894B2 (en) | 2005-08-29 | 2005-08-29 | Impact type work tool |
| JP2005-247679 | 2005-08-29 | ||
| JP2005247679 | 2005-08-29 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1915606A true CN1915606A (en) | 2007-02-21 |
| CN1915606B CN1915606B (en) | 2010-05-12 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2006101110714A Active CN1915606B (en) | 2005-08-19 | 2006-08-18 | Impact power tool |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4509890B2 (en) |
| CN (1) | CN1915606B (en) |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US7832498B2 (en) | 2007-06-15 | 2010-11-16 | Makita Corporation | Impact tool |
| US8087474B2 (en) | 2007-04-12 | 2012-01-03 | Makita Corporation | Hammer drill |
| CN102343576A (en) * | 2010-08-02 | 2012-02-08 | 株式会社牧田 | Impact tool |
| CN102387899A (en) * | 2009-04-10 | 2012-03-21 | 株式会社牧田 | Striking tool |
| CN101801611B (en) * | 2007-09-13 | 2012-09-19 | 株式会社牧田 | Impact tool |
| CN102862149A (en) * | 2011-07-05 | 2013-01-09 | 罗伯特·博世有限公司 | Impact mechanism device |
| CN105612030A (en) * | 2013-10-03 | 2016-05-25 | 喜利得股份公司 | Handheld power tool |
| CN106737437A (en) * | 2017-01-11 | 2017-05-31 | 江苏东成机电工具有限公司 | Hand-held tool |
| CN107914245A (en) * | 2016-10-07 | 2018-04-17 | 株式会社牧田 | Percussion tool |
| CN110468898A (en) * | 2018-05-11 | 2019-11-19 | 山特维克矿山工程机械有限公司 | Tooling sleeve, quartering hammer and installation method |
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| JP5009060B2 (en) * | 2007-06-15 | 2012-08-22 | 株式会社マキタ | Impact tool |
| JP5512393B2 (en) * | 2010-05-25 | 2014-06-04 | 株式会社マキタ | Impact tool |
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| DE4415348A1 (en) * | 1994-05-02 | 1995-11-09 | Hilti Ag | Drilling and chiseling device |
| JPH08318342A (en) * | 1995-05-25 | 1996-12-03 | Makita Corp | Impact tool |
| DE19714288A1 (en) * | 1997-04-07 | 1998-10-08 | Hilti Ag | Drilling and / or chiseling device |
| DE19933972A1 (en) * | 1999-07-20 | 2001-01-25 | Bosch Gmbh Robert | Hammer drill or hammer |
| PT1238759E (en) * | 2001-03-07 | 2004-04-30 | Black & Decker Inc | HAMMER |
| DE10130088C2 (en) * | 2001-06-21 | 2003-10-16 | Hilti Ag | Striking electric hand tool device with active vibration damping |
| JP4276095B2 (en) * | 2004-01-26 | 2009-06-10 | 株式会社マキタ | Work tools |
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| JP4155857B2 (en) * | 2003-04-01 | 2008-09-24 | 株式会社マキタ | Work tools |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8087474B2 (en) | 2007-04-12 | 2012-01-03 | Makita Corporation | Hammer drill |
| CN101657300B (en) * | 2007-04-12 | 2012-12-26 | 株式会社牧田 | Hammer drill |
| US7832498B2 (en) | 2007-06-15 | 2010-11-16 | Makita Corporation | Impact tool |
| CN101801611B (en) * | 2007-09-13 | 2012-09-19 | 株式会社牧田 | Impact tool |
| CN102387899B (en) * | 2009-04-10 | 2015-06-24 | 株式会社牧田 | Striking tool |
| CN102387899A (en) * | 2009-04-10 | 2012-03-21 | 株式会社牧田 | Striking tool |
| CN102343576B (en) * | 2010-08-02 | 2013-11-20 | 株式会社牧田 | Impact tool |
| CN102343576A (en) * | 2010-08-02 | 2012-02-08 | 株式会社牧田 | Impact tool |
| CN102862149A (en) * | 2011-07-05 | 2013-01-09 | 罗伯特·博世有限公司 | Impact mechanism device |
| CN105612030B (en) * | 2013-10-03 | 2018-05-08 | 喜利得股份公司 | Hand held power machine |
| CN105612030A (en) * | 2013-10-03 | 2016-05-25 | 喜利得股份公司 | Handheld power tool |
| US11878401B2 (en) | 2013-10-03 | 2024-01-23 | Hilti Aktiengesellschaft | Handheld power tool |
| CN107914245A (en) * | 2016-10-07 | 2018-04-17 | 株式会社牧田 | Percussion tool |
| CN107914245B (en) * | 2016-10-07 | 2022-02-01 | 株式会社牧田 | Impact tool |
| CN106737437A (en) * | 2017-01-11 | 2017-05-31 | 江苏东成机电工具有限公司 | Hand-held tool |
| CN110468898A (en) * | 2018-05-11 | 2019-11-19 | 山特维克矿山工程机械有限公司 | Tooling sleeve, quartering hammer and installation method |
| CN110468898B (en) * | 2018-05-11 | 2022-09-06 | 山特维克矿山工程机械有限公司 | Tool bushing, breaking hammer and mounting method |
| US11478914B2 (en) | 2018-05-11 | 2022-10-25 | Sandvik Mining And Construction Oy | Tool bushing, breaking hammer and mounting method |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2007050495A (en) | 2007-03-01 |
| CN1915606B (en) | 2010-05-12 |
| JP4509890B2 (en) | 2010-07-21 |
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