CN201067814Y - Hammer drill - Google Patents
Hammer drill Download PDFInfo
- Publication number
- CN201067814Y CN201067814Y CNU2006201122492U CN200620112249U CN201067814Y CN 201067814 Y CN201067814 Y CN 201067814Y CN U2006201122492 U CNU2006201122492 U CN U2006201122492U CN 200620112249 U CN200620112249 U CN 200620112249U CN 201067814 Y CN201067814 Y CN 201067814Y
- Authority
- CN
- China
- Prior art keywords
- clutch
- hammer drill
- axle
- percussion movement
- drill bit
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Images
Landscapes
- Percussive Tools And Related Accessories (AREA)
Abstract
A hammer drill comprises a motor, a mandrel, a movement transformation component, an impact body, a relieving device of impact movements and a regulating clutch of a winding torque; wherein, the mandrel which is driven by the rotation of the motor keeps an output drill; the movement transformation component is used for transforming the rotational movements of the motor into reciprocating movements; the impact body is driven in a reciprocating way by the movement transformation component so as to impose axial impact force to the output drill; the relieving device of impact movements is used for relieving the imposing movements of the impact force implemented by the impact body; the regulating clutch of a winding torque is used for interrupting the transfer of rotating force to the output drill by increasing a loading torque. The hammer drill of the utility model can not only execute the working model of transferring only the rotating force to the output drill but also allows the users to control a screw winding torque by using the regulating clutch of a winding torque.
Description
Technical field
The utility model relates to hammer drill, and it is adapted to pass through impacting body that use produces by the motion conversion member and moves back and forth and apply axial impact power on the output drill bit that rotation drives.
Background technology
Hammer drill is used to carry out, for example the work of drilling concrete structure.So the situation on the anchor can occur screw threads need being tightened to, wherein anchor embeds in the hole that forms by bore operation.Yet therefore the typical hammer drill percussion movement that invariably accompanies can not be used to screw screw, and this just needs to use in addition electric screw driver.
What be known in the art in addition is the sort of hammer drill that can remove percussion movement and only revolving force be passed to the output drill bit.This hammer drill does not have ability to screw screw with suitable moment of torsion, but often easy excessive screwing screw.
Simultaneously, the flat 7-1355 communique of TOHKEMY 2000-233306 communique and Te Kai discloses vibration and has bored and percussion drill, wherein can remove oscillating load or impact load and screw moment of torsion and can use and screw the torque adjustment clutch and control.Yet, up to now, drive also not use in the hammer drill on the output drill bit and screw the torque adjustment clutch axial impact power being applied to rotation by using the axially reciprocating impacting body.Therefore, traditional hammer drill still needs to use electric screw driver to carry out the aforesaid work that screws screw.
The utility model content
In order to overcome problems of the prior art, the purpose of this utility model provides and a kind ofly can stop the axial impact motion and can allow the user to use screwing the hammer drill that torque adjustment Clutch Control screw screws moment of torsion.
According to the utility model, a kind of hammer drill of operating under percussion movement originate mode and percussion movement stop mode is provided, it comprises: motor, by motor rotation drive and keeping export drill bit axle, be used for rotatablely moving of motor changed into reciprocating motion conversion member, back and forth driven by the motion conversion member, to apply the impacting body of axial impact power and to screw the torque adjustment clutch to exporting drill bit.Screwing the torque adjustment clutch comprises: rotary body, and it is driven by described motor rotation, and has a plurality of axial penetration holes that holding steel ball; Clutch plate, it is configured to rotate as a whole with described axle, and has the depression of the described steel ball of a plurality of maintenances; And clutch spring, it applies engaging force between described steel ball and described depression.At described percussion movement stop mode, under the state of load torque greater than described engaging force, described steel ball breaks away from described depression, to limit the described moment of torsion that screws that screws the torque adjustment clutch.According to hammer drill of the present utility model the beneficial effect that can obtain be, both can carry out and have only revolving force to pass to the mode of operation of output drill bit, can allow the user to use again simultaneously to screw torque adjustment Clutch Control screw to screw moment of torsion.This makes single hammer drill can carry out two kinds of work, promptly bores target object, as the work of xoncrete structure etc., and the work that screws screw.
Description of drawings
Can be expressly understood very much above-mentioned and other purpose and feature of the present utility model by reading for the explanation of preferred embodiment below in conjunction with accompanying drawing, wherein:
Fig. 1 is the vertical cutaway view according to the hammer drill of first preferred embodiment of the utility model;
Fig. 2 is the vertical cutaway view of hammer drill shown in Figure 1, and it is set in the percussion movement originate mode;
Fig. 3 is the vertical cutaway view of the local excision of hammer drill shown in Figure 1, and it is set in the percussion movement originate mode;
Fig. 4 by graphic representation the feature of employed clutch in the hammer drill shown in Figure 1;
Fig. 5 is the vertical cutaway view according to the hammer drill of second preferred embodiment of the utility model, and it is set in the percussion movement originate mode;
Fig. 6 is the decomposition diagram that screws the torque adjustment clutch that shows hammer drill shown in Figure 5;
Fig. 7 A and Fig. 7 B are the cutaway views that screws the work of coupling part in the torque adjustment clutch that shows hammer drill shown in Figure 5;
Fig. 8 is the vertical cutaway view of hammer drill shown in Figure 5, and it is set in the percussion movement stop mode;
Fig. 9 A shows that switching handle, the axle collar and motion in the duty change the top view of parts, and Fig. 9 B shows the front view that switches handle;
Figure 10 A shows that switching handle, the axle collar and motion in another duty change the top view of parts, and Figure 10 B shows the front view that switches handle;
Figure 11 is the front view that screws the rotary body in the torque adjustment clutch that shows hammer drill shown in Figure 5;
Figure 12 is that it is set in the percussion movement originate mode according to the vertical cutaway view of the hammer drill of the 3rd preferred embodiment of the utility model;
Figure 13 is the vertical cutaway view of hammer drill shown in Figure 12, and it is set in the percussion movement stop mode;
Figure 14 shows the clutch handle of hammer drill shown in Figure 12 and the perspective view of action bars;
Figure 15 is the expanded view of engaging groove that shows the clutch handle of hammer drill shown in Figure 12;
Figure 16 is that it is set in the percussion movement originate mode according to the vertical cutaway view of the hammer drill of the 4th preferred embodiment of the utility model;
Figure 17 is the vertical cutaway view of hammer drill shown in Figure 16, and it is set in the percussion movement stop mode;
Figure 18 shows the clutch handle of hammer drill shown in Figure 16 and the perspective view of action bars;
Figure 19 is the expanded view of cam path that shows the clutch handle of hammer drill shown in Figure 16;
Figure 20 is that it is set in the percussion movement stop mode according to the vertical cutaway view of the hammer drill of the 5th preferred embodiment of the utility model;
Figure 21 is the horizontal cross of hammer drill shown in Figure 20, and it is set in the percussion movement stop mode;
Figure 22 is the vertical cutaway view of hammer drill shown in Figure 20, and it is set in the percussion movement originate mode;
Figure 23 is the horizontal cross of hammer drill shown in Figure 20, and it is set in the percussion movement originate mode;
Figure 24 is the side view of hammer drill shown in Figure 20;
Figure 25 A to Figure 25 D is the cutaway view that is obtained along Figure 24 cathetus 25A-25A, 25B-25B, 25C-25C and 25D-25D respectively;
Figure 26 is the decomposition diagram that screws the torque adjustment clutch that shows hammer drill shown in Figure 20;
Figure 27 A is the perspective view of connector, and Figure 27 B is the perspective view that shows the typical SDS-plus handle of output drill bit; With
Figure 28 is the partial sectional view that shows the remodeling example of bracket portion.
The specific embodiment
Embodiment shown in inciting somebody to action in conjunction with the accompanying drawings now illustrates the utility model.According to first preferred embodiment of the present utility model, connecting axle 13 is connected with output shaft 10 operability of motor with 12 by gear 11, as shown in fig. 1.Connecting axle 13 is provided with pinion 14 integrally formed with it at its front end.Motion conversion member 2 is arranged on the mid portion of connecting axle 13.
When the steel ball 42 in remaining on rotary body 40 holes engages with the depression of clutch plate 41, rotary body 40, is guaranteed by rotary body 40 and clutch plate 41 revolving force of connecting axle 13 to be passed to cylinder barrel 3 as a whole around the rotation of the axis of cylinder barrel 3 with clutch plate 41 thus.
At one end keep circle 44 clutch springs that contact 45 to support by the removable plate 46 that the periphery around cylinder barrel 3 is provided with at the other end with steel ball.Be accompanied by the rotation of clutch handle 48, removable plate 46 can change the compression degree of clutch spring 45 thus along the axially-movable of cylinder barrel 3.
Axle 5 is connected with the axial forward end of cylinder barrel 3 and is used for carrying out the integral body rotation with cylinder barrel 3.Axle 5 is provided with chuck part 51 in its axial forward end and is used for keeping output drill bit 50 in following mode, promptly exports drill bit 50 and can rotate as a whole and can endwisely slip in limited range of motion with chuck part 51.
Axle 5 also is provided with ball 56 and ball 57, and wherein ball 56 is used to stop the intermediate members 52 that remain in the axle 5 in axial slidably mode to shift out backward, and ball 57 is used for the retraction movement at a certain position restriction intermediate member 52 of ball 56 fronts.As shown in fig. 1, only when being positioned at around the ball 57 with removable plate 46 integrally formed limited parts 47, ball 57 just is used to limit the retraction movement of intermediate member 52.If therefore rotary clutch handle 48 also removes limited part 47 with the removable plate 46 of withdrawing around ball 57, as shown in Figure 2, so when output drill bit 50 is crushed on the boring object, the intermediate member 52 that its front end remained and exported the back end in contact of drill bit 50 will radially promote ball 57 backward, and move backward and contact, as shown in Figure 3 for shifting out ball 56 with prevention.
Piston 30 is for having the cylindrical of closed rear end and open forward end.Impacting body 35 is slidably received within the piston 30.When piston 30 moved back and forth, impacting body 35 also produced reciprocating motion, and the air that be enclosed in the interior volume of piston 30 by impacting body 35 this moment plays the effect of air spring.Being arranged on interior week of axle 5 rear end parts is O type circle 58, and the periphery resilient engagement of this O type circle and impacting body 35 fore-ends is used to stop impacting body 35 to move backward.
Under state shown in Figure 1, promptly the limited part 47 at removable plate 46 is placed under ball 57 situation on every side, and the motion backward of intermediate member 52 is restricted.In addition, be maintained at impacting body 35 under the state of axle 5 rear end parts, the revolving force of motor passes to cylinder barrel 3 via rotary body 40 and clutch plate 41 from connecting axle 13, passes to output drill bit 50 by axle 5 from cylinder barrel 3 then.
Meanwhile, rotatablely moving of connecting axle 13 changed the reciprocating motion of piston 30 into by motion conversion member 2.Therefore at this moment, impacting body 35 is maintained by axle 5, and therefore, impacting body 35 can not carry out any reciprocating motion, and only rotatablely moves and be applied in to output drill bit 50.
When using rotation output drill bit 50 to screw the work of screw for example, if load torque becomes greater than the engaging force between the depression of steel ball 42 that is produced by clutch spring 45 and clutch plate 41, steel ball 42 will leave depression so, stops the revolving force of rotary body 40 to be delivered to clutch plate 41 (cylinder barrel 3) thus.This has limited and has screwed moment of torsion (tightening torque).
To such an extent as to can move backward to increase by rotary clutch handle 48 removable plates 46 in the manner described above and screw moment of torsion with the compression degree that increases clutch spring 45.This means that rotary body 40 and clutch plate 41 and steel ball 42, removable plate 46 and clutch spring 45 synergies screw torque adjustment clutch 4 with formation.In addition, bulb-shaped recess is formed at steel ball and keeps on the circle 44 rolling on the part that contacts with steel ball 42.
If the motion backward by removable plate 46 is removed limited part 47 around ball 57, as shown in Figure 2, output drill bit 50 and intermediate member 52 move backward when output drill bit 50 is crushed on the boring object so, and edge direction backward promotes impacting body 35 thus, as shown in Figure 3.So the reciprocating motion of piston 30 causes the reciprocating motion of impacting body 35, this means impacting body 35 be in by intermediate member 52 vertically impact is imposed on output drill bit 50 state in.And, screw torque adjustment clutch 4 and be designed to have the moment of torsion that screws when moving rearwards to above-mentioned position, this means that screwing torque adjustment clutch 4 constitutes safety clutch (referring to Fig. 4) greater than motor stalling torque (the free driving torque of clutch) at limited part 47 (removable plate 46).
Fig. 5 to Figure 11 has shown the hammer drill according to second preferred embodiment of the utility model.Although the percussion movement stop mode that does not wherein have impact to impose on output drill bit 50 is to realize by the motion that stops impacting body 35 in first preferred embodiment, identical pattern is to realize from the revolving force that connecting axle 13 passes to motion conversion member 2 by interruption in second preferred embodiment.More particularly, the rotating part 20 of motion conversion member 2 is manufactured into and can rotates with respect to connecting axle 13.Wherein provide and rotating part 20 synergy forming the axle collar 15 of engaging clutch, to such an extent as to the axle collar 15 can rotate as a whole and can slide vertically with respect to connecting axle 13 with connecting axle 13.Be pressed on the rotating part 20 by spring 16 under the axle collar 15 normal conditions, pass to rotating part 20 to such an extent as to it can engage the revolving force that is used for connecting axle 13 with rotating part 20.If the axle collar 15 is shifted away from rotating part 20 against the biasing force of spring 16, as shown in Figure 8, just there is not revolving force to pass to rotating part 20, the result stops any reciprocating motion of cylinder barrel 3, does not therefore have impact to impose on output drill bit 50.
With reference to figure 9A to Figure 10 B, the moving through of the axle collar 15 handled the switching handle 7 be exposed to the outside and produced.In the drawings, Reference numeral 70 expression is used to drive the cam bawl of the switching handle 7 of the axle collar 15.
According to second preferred embodiment, the percussion movement originate mode can be converted to the percussion movement stop mode, and vice versa, and no matter the moment of torsion of regulating that screws has much.Therefore, the hammer drill of second preferred embodiment comprises such mechanism, and it screws torque adjustment clutch 4 by use and directly connects the rotation transmission members and make that to screw the torque adjustment function inoperative in the percussion movement originate mode.
This device comprises pin 8, spring 80 and change-over panel 81, wherein sell 8 and be used for directly connecting rotary body 40 that is used as actuator and the clutch plate 41 that is used as driven member, spring 80 is used for pin 8 pressed to direct coupled position takes place, and change-over panel 81 is used for will sell 8 against spring 80 and pushes the direct-connected releasing of releasing position.In the embodiment shown, change-over panel 81 is suitable for the motion interlocking with the axle collar 15.
Specifically, engage carrying out and the percussion movement that rotatablely moves and cooperate in order to make the axle collar 15 and rotating part 20, as shown in Figure 5, to such an extent as to make move backward rotary body 40 and clutch plate 41 of change-over panel 81 can pass through pin 8 and directly connect, as shown in Figure 7A.If shifting forward, the axle collar 15 breaks away from and the engaging of rotating part 20, to such an extent as to change-over panel 81 is just pushed rotary body 40 by the axle collar 15 and clutch plate 41 can carry out relative motion so, as shown in Fig. 7 B.
The hole 402 that being used to of penetrating that rotary body 40 forms held steel ball 42 has the pitch circle that is different from the hole 408 that holds pin 8 and spring 80, as clearly visible among Figure 11.This anti-shotpin 8 shifts out the joint depression of clutch plate 41.
Figure 12 to Figure 15 has shown the hammer drill according to the 3rd preferred embodiment of the utility model.The something in common of the 3rd preferred embodiment and second preferred embodiment is that percussion movement stop mode (referring to Figure 13) is to realize by interrupting the transmission that synergy forms revolving force between the rotating part 20 of engaging clutch and the axle collar 15, and at the percussion movement originate mode, be (referring to Figure 12) in the hammer drill pattern, the rotary body 40 and the clutch plate 41 that screw the torque adjustment clutch directly connect each other by pin 8.Yet,, wherein provide action bars 79 with the axially-movable interlocking of the axle collar 15 according to the 3rd preferred embodiment of the present utility model.One end of action bars 79 engages with engaging groove 480 on being arranged on clutch handle 48.
About this point, engaging groove 480 is the pectination shape, promptly has part and a plurality of part that extends axially of extending along the circumferencial direction of clutch handle 48.At the percussion movement originate mode, promptly in the hammer drill pattern, action bars 79 enters of engaging groove 480 and extends axially part (among Figure 15 " X ") and the locking any manipulation to clutch handle 48.In the percussion movement stop mode, action bars 79 is set at the circumference extension (among Figure 15 " Y ") of engaging groove 480, allows clutch handle 48 to be manually turned thus and make to regulate to screw moment of torsion.
Figure 16 to Figure 19 has shown the hammer drill according to the 4th preferred embodiment of the utility model.The transmission that both form revolving force between the rotating part 20 of engaging clutch and the axle collar 15 is interrupted in response to the manipulation of clutch handle 48.Clutch handle 48 has cam path 481, and an end of action bars 79 engages with described cam path.Screwing under the adjustable state of moment of torsion, action bars 79 causes the axle collar 15 displacements away from rotating part 20, as shown in Figure 17, stops the reciprocating motion of piston 30 thus.Under the contrast, clutch spring 45 is compressed under the maximum state shown in Figure 16, the axle collar 15 engages with rotating part 20 thus revolving force is passed to motion conversion member 2 at rotary clutch handle 48.This causes the percussion movement originate mode, i.e. hammer drill pattern, and wherein impact and revolving force all are applied in to output drill bit 50.At this moment, steel ball 42 can not deviate from clutch plate 41 and move against the extruding force of clutch spring 45, thus revolving force be delivered to output drill bit 50, and no matter load torque be much.
Figure 20 to Figure 28 has shown the hammer drill according to the 5th preferred embodiment of the utility model.The hammer drill of the 5th preferred embodiment is identical to embodiment shown in Figure 11 with Fig. 5 on basic sides.To provide explanation below in order about the hammer drill of the preferred embodiment.Reference numeral 9 expression shells among the figure, grip 90 forms from its downward extension with its integral body.Battery pack 91 is detachably connected to the bottom of grip 90.Shell is strengthened between the front end that coupling part 92 integral body are formed at the bottom front of grip 90 and shell 9.Reference numeral 93 expressions among the figure are arranged on the trigger switch of grip 90 bottoms.Being arranged in the rear end part of shell 9 is motor 19, and described motor can start or stops and can changing its direction of rotation in response to the manipulation of break-in bar 94 by the operation of trigger switch 93.Figure 26 has shown the employed decomposition diagram that screws torque adjustment clutch 4 in the hammer drill of the 5th preferred embodiment.
Connecting axle 13 is connected with output shaft 10 operability of motor 19 with 12 by gear 11.Connecting axle 13 is provided with pinion 14 integrally formed with it at its front end.Motion conversion member 2 is arranged on the mid portion of connecting axle 13.Motion conversion member 2 comprise be fixed on the connecting axle 13 and therewith as a whole the rotating part 20 of rotation, rotatably be installed to outer race 21 on the inclined surface of rotating part 20 and the bar 22 that stretches out from outer race 21.Bar 22 is connected with piston 30, and piston 30 can axially move in cylinder barrel 3 along it.
The axle collar 15 that forms engaging clutches with rotating part 20 synergy is arranged on the connecting axle 13 in following mode, and promptly the axle collar 15 can rotate as a whole and can slide vertically with respect to connecting axle 13 with connecting axle 13.The axle collar 15 is pressed on the rotating part 20 by spring 16 and engages with rotating part 20 thus the revolving force of connecting axle 13 is passed to rotating part 20.When rotating part 20 is rotated when motion, bar 22 and outer race 21 are subjected to the restriction that is connected with piston 30 with respect to the rotation of connecting axle 13, so carry out oscillating movement.This causes piston 30 along its axially reciprocating.
If handle the switching handle 7 (referring to Figure 24) be arranged on shell 9 sides, the axle collar 15 just moves forward against spring 16 and breaks away from rotating part 20.Under this state, do not have revolving force to pass to rotating part 20, and in piston 30, do not cause reciprocating motion.
When the steel ball 42 in remaining on rotary body 40 holes engages with the depression of clutch plate 41, rotary body 40, is guaranteed by rotary body 40 and clutch plate 41 revolving force of connecting axle 13 to be passed to cylinder barrel 3 as a whole around the rotation of the axis of cylinder barrel 3 with clutch plate 41 thus.At one end keep circle 44 clutch springs that contact 45 to support by the removable plate 46 that the periphery around cylinder barrel 3 is provided with at the other end with steel ball.Be accompanied by the rotation of clutch handle 48, removable plate 46 can change the compression degree of clutch spring 45 thus along the axially-movable of cylinder barrel 3.
But change-over panel 81 is arranged on the peripheral of cylinder barrel 3 in the mode of axially-movable.If for moving forward, so directly the far-end of attachment pegs 8 just is placed in the border surface place of rotary body 40 and clutch plate 41 to change-over panel 81 by spring 82 extruding, as shown in Figure 20, remove direct connection the between rotary body 40 and the clutch plate 41 thus.When the axle collar 15 moves when engaging with rotating part 20, change-over panel 81 is pushed by the axle collar 15 and moves backward against spring 82, allows pin 8 that rotary body 40 directly is connected on the clutch plate 41 thus.
Figure 20 and Figure 21 have shown the percussion movement stop mode, promptly are exclusively used in the state that screws screw.In order to obtain this pattern, switch handle 7 axle collar 15 is moved forward by handling, remove engaging between the axle collar 15 and the rotating part 20 thus.Meanwhile, the flange portion 150 of the axle collar 15 is eliminated the motive force that imposes on change-over panel 81, and in response, change-over panel 81 moves forward under the pressure of spring 82 to promote direct attachment pegs 8.This removes direct connection the between rotary body 40 and the clutch plate 41.So, rotary body 40 is passed to axle 5 from the revolving force that the pinion 14 of connecting axle 13 obtains by steel ball 42, clutch plate 41 and cylinder barrel 3.At this moment, be arranged on the front end periphery resilient engagement of the O type circle on week 58 and impacting body 35 in the rear end of axle 5, stop any axially-movable of impacting body 35 and intermediate member 52 thus.Therefore, can by mistake not cause the motion of impacting body 35 and intermediate member 52.
In the percussion movement stop mode, rotate output drill bit 50 by using " screw; for example in the process of screw; if load torque becomes greater than steel ball of being bestowed by clutch spring 45 42 and the engaging force between the clutch plate 41; steel ball 42 will leave the joint depression of clutch plate 41 so, interrupts the revolving force transmission of from rotary body 40 to clutch plate 41 (cylinder barrels 3) thus.This has limited and has screwed moment of torsion.
Can and removable plate 46 be moved backward by rotary clutch handle 48 in the manner described above to increase and screw moment of torsion with the compression degree that increases clutch spring 45.This means that rotary body 40 and clutch plate 41 and steel ball 42, removable plate 46 and clutch spring 45 act synergistically to form torque adjustment clutch 4.When being compressed to clutch spring 45 at utmost by controlled clutch handle 48, steel ball 42 is maintained at it and can not leaves in the state that engages depression.This state is suitable for so-called bore operation.
Under Figure 22 and situation shown in Figure 23, wherein the axle collar 15 is moved backward to engage with rotating part 20 by handling switching handle 7, the axle collar 15 causes change-over panel 81 to move backward against spring 82, guarantees that thus rotary body 40 and clutch plate 41 directly connect by direct attachment pegs 8.Therefore, piston 30 moves back and forth by motion conversion member 2, and cylinder barrel 3 and axle 5 are driven in rotation always simultaneously.At this moment, when output drill bit 50 " when being crushed on the boring object, output drill bit 50 " and intermediate member 52 move backward, promote impacting body 35 along backward direction thus and surpass the position of O type circle 58 impacting body 35 maintenances.So the reciprocating motion of piston 30 causes the reciprocating motion of impacting body 35, this means impacting body 35 be in by intermediate member 52 vertically impact is imposed on output drill bit 50 " state in.This guarantees that revolving force and axial impact power are delivered to output drill bit 50 ".
Switching handle 7 is suitable for making the axle collar 15 displacements to break away from rotating part 20.The pressure of spring 16 be used to make the axle collar 15 towards rotating part 20 move and with its smooth engagement.Spring 16 is designed to have the pressure bigger than the spring 82 of extruding change-over panel 81.In addition, the pressure of spring 82 is greater than the pressure of the spring 80 of the direct attachment pegs 8 of extruding.
Simultaneously, this output drill bit 50 ", as drill or bottle opener drill bit the SDS-plus handle is not set and is used for using with hammer drill, therefore use connector 50 ' to install with SDS-plus handle.Some is different for the SDS-plus handle and typical SDS-plus handle shown in Figure 27 B that use in the connector 50 '.
More particularly, as shown in Figure 27 A, the SDS-plus handle of connector 50 ' and the something in common of typical SDS-plus handle are that connector 50 ' has and are used for and shift out the sliding tray 501 that stops insertion groove 500 that ball 510 engages and rotation transmission inner projection 511 to be slidably engaged with it.The specific characteristic of connector 50 ' is from the axial length of the sliding tray 501 of handle rear end measurement very short.In other words, when being installed to connector 50 ' in the chuck part 51, the insertion depth of connector 50 ' is subjected to the restriction of the stopping function of inner projection 511.This prevents that connector 50 ' from moving to the preceding end in contact with the intermediate member 52 of its rear end backward.
So, even apply the percussion movement originate mode of revolving force and impact at the same time, be by connector 50 ' output drill bit 50 to be installed in the hammer drill pattern ", for example there are not the possibility that impact is imposed on connector 50 ' in drill or bottle opener drill bit yet.This has also got rid of connector 50 ', output drill bit 50 ", for example drill or bottle opener drill bit and with output drill bit 50 " the screw that contacts of far-end etc. damage because of impact shock.In addition, because above-mentioned reason, impacting body 35 continues to remain in the appropriate location by O type circle 58.
Below under the situation, promptly as output drill bit 50 ", when the hammer drill drill bit with typical SDS-plus handle shown in Figure 27 B is installed on the chuck part 51, output drill bit 50 " can move to output drill bit 50 backward " and the degree of back end in contact intermediate member 52.In addition, impacting body 35 can surpass the position that O type circle 58 keeps impacting body 35 to backward shift by intermediate member 52, and in this state, impact and revolving force all are applied in to output drill bit 50 ".
The sliding tray 501 of connector 50 ' not only also is different from the typical shank of tool in shape on length but also in the inner.Inner projection 511 has the front end that is made of smooth inclined surface.Therefore, if the interior end in contact of the sliding tray 501 of the typical shank of tool shown in the front end of inner projection 511 and Figure 27 B, the lateral edges of the inner of sliding tray 501 is with cut.For fear of this situation, the sliding tray 501 of connector 50 ' is designed to have and can carries out the inclination internal end surface 502 that the face face contacts with the front end of inner projection 511.
About this point, connector 50 ' can be stored in when not using in the bracket portion 95 that is provided with in the coupling part 92 of shell 9.As shown in Figure 24 and Figure 25, bracket portion 95 is the dented space form of opening wide to a side of coupling part 92.Bracket portion 95 has latch plate 950, increases depression plate 952 and cavity part 953, wherein latch plate 950 is used to keep the shank of connector 50 ', increase the major diameter chuck part that depression plate 952 is used to hold connector 50 ', cavity part 953 is used at connector 50 ' and connected output drill bit 50 " hold when storing together and export drill bit 50 ".At the opposite side that increases depression plate 952, coupling part 92 has the thickness that reduces and enters space 951 to provide, and can touch the major diameter chuck part of connector 50 ' to take out connector 50 ' by the described finger that enters the space user.
For do not taking out output drill bit 50 " situation under in bracket portion 95 storage have output drill bit 50 " connector 50 ', to export drill bit 50 " front end insert in the cavity part 953; as shown in Figure 25 D; afterwards, the major diameter chuck segment branch of connector 50 ' is contained in increases in the sunk part 952 and the shank of connector 50 ' pushed the seat of latch plate 950 by part.In taking out the process of connector 50 ', as shown in Figure 25 D, output drill bit 50 " might contact-and-connection portion 92 sidewall edge 955, therefore scratch or damage edge 955.Therefore, it is desirable on the sidewall of coupling part 92, provide reinforcement 954, as shown in Figure 28.
In addition, coupling part 92 forms not stretch out forward and surpasses the straight line (referring to Figure 24) that connects battery pack 91 lower ends and hammer drill front end.This is to be used to prevent any damage to coupling part 92 that caused by impact when the place ahead is not intended to drop at hammer drill.
Both can carry out according to hammer drill of the present utility model and to have had only revolving force to pass to the mode of operation of output drill bit, and simultaneously can allow the user to use again to screw torque adjustment Clutch Control screw to screw moment of torsion.This makes single hammer drill might carry out two kinds of work, promptly bores target object, as the work of xoncrete structure etc., and the work that screws screw.
Though described the utility model with reference to preferred embodiment, it will be understood by those skilled in the art that not breaking away from scope of the present utility model can carry out variations and modifications.
Claims (5)
1. hammer drill of operating under percussion movement originate mode and percussion movement stop mode comprises:
Motor;
Drive and keeping exporting the axle of drill bit by the motor rotation;
Change rotatablely moving of motor into reciprocating motion conversion member;
Back and forth drive to apply the impacting body of axial impact power to the output drill bit by the motion conversion member;
It is characterized in that described hammer drill comprises also and screw the torque adjustment clutch that the described torque adjustment clutch that screws comprises: rotary body, it is driven by described motor rotation, and has a plurality of axial penetration holes that holding steel ball; Clutch plate, it is configured to rotate as a whole with described axle, and has the depression of the described steel ball of a plurality of maintenances; And clutch spring, it applies engaging force between described steel ball and described depression;
Wherein, at described percussion movement stop mode, under the state of load torque greater than described engaging force, described steel ball breaks away from described depression, to limit the described moment of torsion that screws that screws the torque adjustment clutch.
2. hammer drill according to claim 1 is characterized in that, the described torque adjustment clutch that screws directly connects driving side with slave end under described percussion movement originate mode.
3. hammer drill according to claim 1 and 2 is characterized in that, also comprises regulating the described clutch handle that screws moment of torsion, and the device that under described percussion movement originate mode, locks described clutch handle.
4. hammer drill according to claim 1 and 2, it is characterized in that, also comprise the axle collar, it is driven by described motor rotation, and engage the rotating part of described motion conversion member releasedly, under described percussion movement originate mode, to engage described motion conversion member and to transmit revolving force to it.
5. hammer drill according to claim 1 and 2, it is characterized in that, the impact load transmission member that also comprises axially-movable, and under described percussion movement stop mode, keep the restraint device of described impact load transmission member with the axially-movable that limits described impact load transmission member.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2005154701 | 2005-05-26 | ||
| JP154701/2005 | 2005-05-26 | ||
| JP357011/2005 | 2005-12-09 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201067814Y true CN201067814Y (en) | 2008-06-04 |
Family
ID=37442498
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2006201122492U Expired - Fee Related CN201067814Y (en) | 2005-05-26 | 2006-05-26 | Hammer drill |
| CNB2006100899179A Expired - Fee Related CN100420531C (en) | 2005-05-26 | 2006-05-26 | Hammer drill |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2006100899179A Expired - Fee Related CN100420531C (en) | 2005-05-26 | 2006-05-26 | Hammer drill |
Country Status (1)
| Country | Link |
|---|---|
| CN (2) | CN201067814Y (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104918570A (en) * | 2012-11-14 | 2015-09-16 | 不列颠哥伦比亚癌症机构分部 | A drill attachment for cannulated surgical drills |
| CN107000182A (en) * | 2014-11-20 | 2017-08-01 | 喜利得股份公司 | Control method for percussive drill |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5479023B2 (en) * | 2009-10-20 | 2014-04-23 | 株式会社マキタ | Rechargeable power tool |
| DE102010002672A1 (en) * | 2010-03-09 | 2011-09-15 | Robert Bosch Gmbh | hammer drill device |
| CN102267129A (en) * | 2011-07-01 | 2011-12-07 | 浙江海王电器有限公司 | Double-function light type electric hammer |
| CN104708600A (en) * | 2015-03-18 | 2015-06-17 | 江苏源通电气有限公司 | Multi-purpose drilling machine for protecting drilling head |
| CN105569558A (en) * | 2016-03-07 | 2016-05-11 | 湖州中辰建设有限公司 | Percussion drill with pneumatic piston device |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3504650C2 (en) * | 1985-02-12 | 1994-01-20 | Bosch Gmbh Robert | Hammer drill with increased actuation force for the coupling of the impact drive |
| JPH0785842B2 (en) * | 1988-07-15 | 1995-09-20 | 松下電工株式会社 | Hammer drill |
| JP3688943B2 (en) * | 1999-08-26 | 2005-08-31 | 株式会社マキタ | Hammer drill |
| DE10106034B4 (en) * | 2001-02-09 | 2009-11-26 | Robert Bosch Gmbh | Hand tool |
| DE10312980B4 (en) * | 2003-03-24 | 2018-05-03 | Robert Bosch Gmbh | Rotary hammer or impact drill |
| CN2661382Y (en) * | 2003-12-02 | 2004-12-08 | 苏州宝时得电动工具有限公司 | Hammer anvil |
-
2006
- 2006-05-26 CN CNU2006201122492U patent/CN201067814Y/en not_active Expired - Fee Related
- 2006-05-26 CN CNB2006100899179A patent/CN100420531C/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104918570A (en) * | 2012-11-14 | 2015-09-16 | 不列颠哥伦比亚癌症机构分部 | A drill attachment for cannulated surgical drills |
| CN104918570B (en) * | 2012-11-14 | 2017-07-28 | 不列颠哥伦比亚癌症机构分部 | Brill accessory for tubulose surgical drill |
| CN107000182A (en) * | 2014-11-20 | 2017-08-01 | 喜利得股份公司 | Control method for percussive drill |
| CN107000182B (en) * | 2014-11-20 | 2019-09-06 | 喜利得股份公司 | Control method for percussive drill |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100420531C (en) | 2008-09-24 |
| CN1868643A (en) | 2006-11-29 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN201067814Y (en) | Hammer drill | |
| CN200977567Y (en) | Electric impact tool | |
| CN201419268Y (en) | Multimodal drill and speed changer subassembly | |
| CN200977641Y (en) | Connector for electric percussion tool | |
| CN201423460Y (en) | Multi-mode drill with electronic switch device | |
| EP1726407B1 (en) | Hammer drill | |
| US4763733A (en) | Hammer drill with rotational lock | |
| CN201425083Y (en) | Multi-speed drilling machine and speed changer with low-speed gear and single clutch | |
| EP1050381B1 (en) | Impact rotary tool | |
| CN201537724U (en) | Multi-mode hammer drill with conversion and locking devices | |
| US7494437B2 (en) | Impact power tool | |
| EP1563960B1 (en) | Impact driver having a percussion application mechanism which operation mode can be selectively switched between percussion and non-percussion mode | |
| CN101994778B (en) | For the automatic transmission of power tool | |
| EP1714745A2 (en) | Mode selector mechanism for an impact driver | |
| CN102448673B (en) | Electric tool | |
| US20130180745A1 (en) | Mechanical assembly for a power tool | |
| EP2055440B1 (en) | Multi-function double-speed rotary hammer | |
| CN101663134A (en) | Rotary power tool operable in either an impact mode or a drill mode | |
| EP1834735A2 (en) | Electric power tool with a torque limiter | |
| NO179666B (en) | Electrically powered hand tools | |
| CN101327526A (en) | Anti-loose high-clamping force tool machine cutter holder chuck | |
| CN207747002U (en) | The operating mode switching mechanism of electric hammer | |
| JP3134683U (en) | High torque impact structure of power tools | |
| JP5857267B2 (en) | Electric tool |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C17 | Cessation of patent right | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20080604 Termination date: 20110526 |