CN102335907A - Power tool - Google Patents
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- CN102335907A CN102335907A CN2010102395125A CN201010239512A CN102335907A CN 102335907 A CN102335907 A CN 102335907A CN 2010102395125 A CN2010102395125 A CN 2010102395125A CN 201010239512 A CN201010239512 A CN 201010239512A CN 102335907 A CN102335907 A CN 102335907A
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Abstract
The invention relates to a power tool, comprising a shell, a motor and a planetary gear speed reduction system, wherein the motor is arranged in the shell and is provided with an output shaft for providing rotary output; the planetary gear speed reduction system comprises a sun gear, a planetary gear meshed on an output gear of the sun gear, an inner gear ring surrounding the planetary gear, moving end teeth, and a selectable rotation stopping member; the inner gear ring is provided with a first position and a second position in an axial direction; at the first position, the inner gear ring is simultaneously meshed with the sun gear and the planetary gear; at the second position, the inner gear ring is meshed with the planetary gear and separated from the sun gear; when the inner gear ring is at the second position, the inner gear ring is meshed with the moving end teeth so as to realize mutual locking in the circumferential direction; and the rotation stopping member is used for locking the circumferential rotary motion of the moving end teeth. Compared with the prior art, the power tool provided by the invention has the advantage that the arrangement and the adjustment of the inner gear ring are simplified by arranging the moving end teeth matched with the inner gear ring.
Description
Technical field
The present invention relates to a kind of power tool, especially a kind of power tool with ring gear of speed handoff functionality.
Background technology
Power tool, especially drill type electric tool have planetary gear reduction system usually, are used for the high rotating speed of the direct tens thousand of commentaries on classics of exporting of motor is reduced to the lower rotating speed that is fit to carry out driller's work.Planetary gear reduction system generally includes planet carrier, planetary gear, and sun gear, ring gear etc., combination repeatedly reduces motor speed between them.
Power tool is towards miniaturization, and multifunctional direction develops, and drill type electric tool begins integrated, has existed on the market to have the screwdriver function simultaneously, creeps into function, the how moving brill of high low speed handoff functionality.Wherein, The switching of screwdriver function and the switching of high speed functions all relate to the state variation of ring gear; Carry out high low speed when switching; Often need ring gear to move axially, when carrying out the switching of screwdriver function, often need lock or allow the rotation of ring gear to change itself and the meshing relation of planetary gear sun gear.Prior art needs two different ring gears carry out two kinds of above-mentioned functions respectively to switch, and two ring gears mean number of elements be difficult to further minimizing and function switching mechanism is provided with difficulty.
Summary of the invention
The objective of the invention is: a kind of simplification that has is provided, the power tool of the function converting system that is easy to regulate.
For realizing above-mentioned purpose, technical scheme of the present invention is: a kind of power tool comprises: housing; Motor is arranged in housing, has the output shaft that rotation output is provided; Planetary gear reduction system; Institute's speed planetary gear deceleration system comprises sun gear, is engaged in the planetary gear of the output gear of sun gear, around the ring gear of said planetary gear; The primary importance and the second place on said ring gear has axially; Mesh said sun gear and said planetary gear simultaneously at said primary importance ring gear, mesh said planetary gear, break away from said sun gear at second place ring gear; Said power tool also comprises the moved end tooth, and tooth engagement in when said ring gear is positioned at the second place and said moved end is upwards to lock in week each other; And the spline part of the motion that rotates in a circumferential direction of optional locking moved end tooth.
Further, comprise in abutting connection with said moved end tooth, the quiet end tooth that axially-displaceable is moving, and towards said moved end the direction of tooth is oppressed the elastic component of quiet end tooth, be provided with the end tooth that matches separately on the end face that said quiet end tooth and moved end tooth lean.
Further, comprise the torsion cover, screw thread is coupled to the spiral cover in the torsion cover, and said elastic component is the torque spring that is connected in said spiral cover, and the said spiral cover of said torsion cover scalable moves axially to regulate the decrement of said torque spring.
Further; Comprise function switching button; Said function switching button drives said spline part and moves with the optional primary importance and the second place of being positioned at, in the motion that rotates in a circumferential direction of said primary importance spline part locking moved end tooth, in the motion that rotates in a circumferential direction of second place spline part permission moved end tooth.
Further, an end face of said moved end tooth is provided with a plurality of keyways of circumferential distribution, and said spline part can move axially with the optional primary importance and the second place of being positioned at.End at said primary importance spline part engages said keyway, breaks away from said keyway at the end of said second place spline part.
Further; Comprise and switch ring, which is provided with screwdriver and switch groove that said spline part is provided with and is arranged in the pin that said screwdriver switches groove; Said function switching button drives said switching ring and rotates to drive said bearing pin to moving, and the spline part is axially moved between the primary importance and the second place.
Further, said function switching button drives said ring gear and moves axially with the optional primary importance and the second place of being positioned at.
Further, in the second place of ring gear, said moved end tooth and said ring gear are through the spline structure engagement.
Compared with prior art, power tool of the present invention has been simplified the setting and the adjusting of ring gear through the moved end tooth that is provided with and ring gear matches.
Description of drawings
Below in conjunction with accompanying drawing the present invention is described further.
Fig. 1 is the multi-functional brill front view of the specific embodiment of the invention
Fig. 2 is the multi-functional brill vertical view of the specific embodiment of the invention.
Fig. 3 is the cutaway view of main apparent direction of the multi-functional brill of the specific embodiment of the invention.
Fig. 4 is the cutaway view of overlooking direction of the multi-functional brill of the specific embodiment of the invention.
Fig. 5 is the decomposing schematic representation of the multi-functional brill of the specific embodiment of the invention.
Fig. 6 is the gear-box stereogram of the multi-functional brill of the specific embodiment of the invention.
Fig. 7 is the second ring gear stereogram of the multi-functional brill of the specific embodiment of the invention.
Fig. 8 is that the multi-functional brill of the specific embodiment of the invention is about impact wrench switching part mechanism stereogram.
Fig. 9 is that the multi-functional brill of the specific embodiment of the invention is about screwdriver switching part mechanism stereogram.
Figure 10 is the switching ring sketch map of impact wrench function of the multi-functional brill of the specific embodiment of the invention.
Figure 11 is the vertical view cutaway drawing of impact wrench function of the multi-functional brill of the specific embodiment of the invention.
Figure 12 is the switching ring sketch map of high speed drill function of the multi-functional brill of the specific embodiment of the invention.
Figure 13 is the vertical view cutaway drawing of high speed drill function of the multi-functional brill of the specific embodiment of the invention.
Figure 14 is that the low speed of the multi-functional brill of the specific embodiment of the invention bores the switching ring sketch map of function.
Figure 15 is that the low speed of the multi-functional brill of the specific embodiment of the invention bores the vertical view cutaway drawing of function.
Figure 16 is the switching ring sketch map of screwdriver function of the multi-functional brill of the specific embodiment of the invention.
Figure 17 is that the master of screwdriver function of the multi-functional brill of the specific embodiment of the invention looks cutaway view.
1 multi-functional brill 37 middle covers 693 second end teeth
3 housings, 39 bearings, 695 accepting grooves
5 handles, 41 first planet carriers, 70 bearings
7 power brick, 411 pedestals, 71 spiral covers
9 chucks, 413 planetary gear fulcrums, 711 protruded stigmas
10 axis, 43 first planetary gears, 73 torque springs
11 switches, 45 sun gears, 75 quiet end teeth
13 torsion covers, 47 second planet carriers, 751 columns
15 switching-over buttons, 473 slide rails, 753 end teeth
17 function switching buttons, 49 second planetary gears, 77 moved end teeth
171 switch spring 51 first ring gears 771 keyways
173 fore-sets, 53 second ring gears, 773 end teeth
19 switch window 531 splines 775 internal splines
21 motors, 533 annular grooves 81 switch ring
Hit spanner in 23 in output shaft 61 main shafts 811 and switch groove
25 outer output shafts 63 initiatively impact block 813 speed switch groove
V-shaped groove 815 screwdrivers switch groove in 251 supports 631
253 axle sleeves, 633 first end teeth, 83 impact wrench switch pieces
255 pads, 635 clutch slot, 85 speed switch pieces
Hit spring 87 screwdriver switch pieces in 27 axle beds 65
29 output gears, 611 outer V-shaped groove 871 springs
31 gear-boxes, 67 spin, 89 clutch parts
33 fore shells, 69 passive impact block 891 annular grooves
35 back covers, 691 working shafts, 893 slide blocks
895 clutch blocks
The specific embodiment
What Fig. 1 was extremely shown in Figure 17 is a kind of specific embodiment of power tool of the present invention, and this power tool is specially a kind of multi-functional brill 1.Multi-functional brill 1 has the impact wrench function, the high speed drill function, and low speed bores function, the screwdriver function, wherein high speed drill function and low speed brill function also can be referred to as and creep into function.
As shown in Figure 1, multi-functional brill 1 is similar to pistol-shaped, comprises the housing 3 that is tubular basically, with handle 5 and dismountable power brick 7 that is arranged at handle 5 bottoms of housing 3 angled layouts.Housing 3 has longitudinal axis 10.
The front end of housing 3 is provided with the chuck 9 that is used for the clamping working head; Be used for difference clamping different working head (not shown) when this multi-functional brill 1 is realized difference in functionality; Like clamping fastener head when realizing the impact wrench function, clamping fluted drill when realizing that high speed drill function or low speed bore function.Chuck 9 outsides are provided with torsion cover 13, and torsion cover 13 can rotate the max. output torque that is in the multi-functional brill 1 of screwdriver function with adjusting around axis 10.The upper part of handle 5 is provided with the switch 11 that is used to open and close multi-functional brill 1.The interface portion of handle 5 and housing 3 also is provided with switching-over button 15.Multi-functional brill 1 has two switching-over buttons 15, lays respectively at the both sides of housing.
See figures.1.and.2, the top of housing 3 is provided with function switching button 17, and function switching button 17 is arranged in the switching window 19 that is located at housing 3 tops and circumferentially extends.Switch window 19 along circumferentially being furnished with four predeterminated positions successively by end to end.Function switching button 17 can move between these four predeterminated positions, successively multi-functional brill 1 is placed the impact wrench function, the high speed drill function, and low speed bores function, screwdriver function.Switch on the window 19 or the correspondence position of housing 3 is provided with sign, to indicate described four predeterminated positions and its corresponding function.
Below introduce the internal structure of multi-functional brill 1 in detail.
Like Fig. 3, an end that belongs to housing 3 upper grips 9 is a front end, and the relative other end is the rear end.The rear end of housing 3 contains power source, is specially a direct current motor 21.Motor 21 has output shaft and rotatablely moves with output.In this specific embodiment, output shaft 23 and outer output shaft 25 in output shaft comprises.Interior output shaft 23 is by motor 21 driven rotary, and outer output shaft 25 is sleeved on the interior output shaft 23 through interference fit, can be by interior output shaft 23 driven rotary.Outer output shaft 25 has the front and rear that lengthwise extends.Outer output shaft 25 comprises axle bed 27 and output gear 29, and axle bed 27 is positioned at the rear portion of outer output shaft 25, is set on the interior output shaft 23; Output gear 29 is positioned at the front portion of outer output shaft 25, is used for through gear structure the power rotation of motor 21 being exported to the deceleration system of multi-functional brill 1.The length of axle bed 27 and diameter are all greater than output gear 29.
Output shaft extend in the gear-box 31, and the housing of gear-box 31 comprises fore shell 33 and back cover 35, and they fasten and form receiving space, contain planetary gear reduction system and power output system.
In conjunction with Fig. 3, Fig. 4, Fig. 5, planetary gear reduction system is a double reduction system; Specifically comprise first planet carrier, 41, the first planetary gears 43, sun gear 45, the second planet carriers 47; Second planetary gear 49, and two ring gears are respectively first ring gear 51 and second ring gear 53.
Pedestal 411 centers are through hole, and pedestal 411 is installed and is supported on the axle bed 27 of output shaft through this through hole.Also be provided with support system between pedestal 411 and the axle bed 27; Specifically comprising one, to be enclosed within motor output shaft outer, and step-like support 251, one are arranged on the axle sleeve 253 between the through-hole wall of support 251 and pedestal 411 and are arranged on the rear end of pedestal 411 and the pad 255 between the gear-box inwall bottom.This support system so that first planet carrier 41 can be good with respect to axle bed 27 rotation.It should be noted that; In the present embodiment; The major part of the pedestal 411 of first planet carrier is supported on the axle bed 27, and the length of this axle bed 27 is longer, and promptly the effective length that supports of the supported parts of first planet carrier 41 is longer; This can stablize the planet carrier 41 of winning, and high speed is rotated and can significantly do not worn and not torn or lose efficacy for a long time.
Planetary gear fulcrum 413 stretches out from the front end of pedestal 411, and one first planetary gear 43 is installed on each planetary gear fulcrum 413.The number of planetary gear fulcrum 413 and planetary gear 43 is corresponding in this specific embodiment is 3.First planetary gear 43 and output gear 29 engagements are by its drive star gear fulcrum 413 rotations of detouring.The internal tooth engagement of 43 whiles of first planetary gear and first ring gear 51.First ring gear 51 fixedly installs with respect to gear-box 31.
The end of planetary gear fulcrum 413 reaches the front of first planetary gear 43.Sun gear 45 comprises toothed disc and gear shaft.Be equipped with tooth on the side face of toothed disc and gear shaft.Have plurality of holes on the toothed disc, the position of its position and quantity and planetary gear fulcrum 413 and quantity are corresponding, sun gear 45 is installed to the end of planetary gear fulcrum 413.Around the gear shaft around be furnished with a plurality of second planetary gears 49 with the gear shaft engagement.The concrete quantity of second planetary gear 49 is 5, is sleeved on one by one on the planetary gear fulcrum of respective amount of second planet carrier 47.Second planet carrier 47 is fixedly connected power output system.
The outside that the footpath of the sun gear 45 and second planetary gear 49 makes progress is provided with second ring gear 53.And the end tooth of the sun gear 45 and second planetary gear 49 all can be engaged in the internal tooth of second ring gear 53.Second ring gear 53 can move forward and backward with respect to gear-box 31 in the axial direction, has position behind a front position and.In the front position, second ring gear 53 and 49 engagements of second planetary gear, and break away from sun gear 45; And second ring gear 53 can not rotate in the front position, and promptly week is upwards fixed with respect to gear-box.In the position, back, second ring gear meshes the end tooth of the gear ring of second planetary gear 49 and sun gear 45 simultaneously; And back position second ring gear can be around axis 10 rotations, and promptly week is upwards movable with respect to gear-box.
Introduce the moderating process of planetary gear reduction system below in detail.
Referring to 3, Fig. 4, Fig. 5, Fig. 6, Fig. 9, the rotation of the output shaft of motor 21 drives star-wheel fulcrum 413 rotations of detouring of first planetary gear 43, and first planetary gear 43 is creeped along the internal tooth of the ring-type of first ring gear 51 simultaneously, around axis 10 revolution.The revolution of first planetary gear 43 drives first planet carrier 41 around axis 10 rotations.Sun gear 45 is connected with first planet carrier 41 through three planetary gear fulcrums 413, thereby with 41 rotations of first planet carrier.More than be the first order moderating process of planetary gear reduction system.In this process; The high speed rotation of output shaft output is by the preliminary reduction of first planetary gear 43; Its speed reducing ratio is the inverse ratio of the number of teeth of the number of teeth and first planetary gear 43 of the output gear 29 of output shaft, and in the present embodiment, the gear ratio of the output gear 29 and first planetary gear 43 is 7: 18.In order to reach more excellent deceleration effect, this gear ratio preferably should be less than 1: 2.The rotating speed that less gear ratio has reduced by first planetary gear 43 is set, has further improved the stability of deceleration system, simultaneously; Be provided with long axle bed 27 and not only improved the stability that supports, also make the planetary gear 43 of winning be arranged on position more forward in the gear-box 31, forward position is than the bottom of gear-box; The space that the footpath makes progress is bigger; The first bigger planetary gear 43 of this also feasible setting, and then more tooth is set, finally obtaining less gear ratio becomes possibility.In this process, first planetary gear 43 is around axis 10 revolution, and 45 rotations have reduced the rotation output speed to power output system for the second time with sun gear to drive first planet carrier 41.
Rotatablely move output to sun gear 45 after, according to former and later two positions of second ring gear 53, to two kinds of deceleration situations should be arranged.When second ring gear 53 is positioned at the front position; Second ring gear 53 is optional does not rotate and breaks away from sun gear; Thereby the gear shaft of sun gear 45 drives second planetary gear 49 around the rotation of the planetary gear fulcrum of second planet carrier 47, and on the internal tooth of second ring gear 53, creeps, around axis 10 revolution; And then drive second planet carrier 47 around axis 10 rotations, will rotatablely move is delivered to power output system.This process has formed the second level deceleration of planetary gear reduction system.When second ring gear 53 is positioned at the back during position, second ring gear 53 is rotatable and mesh the toothed disc and second planetary gear 49 of sun gear 45 simultaneously.Therefore, the rotating tee of sun gear 45 is crossed second ring gear 53 and is delivered to second planetary gear 49 and second planet carrier 47, slows down and be cancelled in the second level.
To sum up, the planetary gear reduction system of present embodiment can be exported two kinds of different rotating speed.Yet, this planetary gear reduction system improved to make it to provide the output of more different rotating speed be possible.For example; First ring gear 51 is arranged to have and second ring gear, 53 similar front positions and position, back, makes it mesh first planetary gear 43 and sun gear 45 can be optional the time, or only mesh first planetary gear 43; Make up the front and back position relation of first ring gear 51 and second ring gear 53 then; At least 3 kinds of rotating speed outputs promptly can be provided, and setting that it is concrete and compound mode are that those skilled in the art are easy to according to the thought of foregoing description design, and are not giving unnecessary details at this.
The bonding part of fore shell 33 and back cover 35 also is provided with middle cover 37, and middle cover 37 is divided into former and later two parts with gear-box 31, and the rear section mainly holds planetary gear reduction system, and forward part is mainly held power output system.Ring is equipped with bearing 39 in the middle cover 37, and bearing 39 supports second planet carrier 47.
The power output system of this specific embodiment below is detailed.
Like Fig. 3, Fig. 4, Fig. 5, Fig. 7, Fig. 8, foregoing, second planetary gear 47 is fixedly connected with power output system, and is concrete, and second planet carrier 47 and main shaft 61 are fixedly connected through interference fit, and main shaft 61 is followed 47 rotations of second planet carrier all the time.
Power output system comprises that one is set in the active impact block 63 on the main shaft 61, the spin V-shaped groove beater mechanism of being located at the impact spring 65 between the active impact block 63 and second planet carrier 47 and being positioned at active impact block 63 and main shaft 61 joints; Wherein this beater mechanism is included in the outer V-shaped groove 611 that main shaft 61 surfaces are recessed to form; The spin 67 of rolling in the V-shaped groove 611 outside; Be steel ball in this embodiment and be located at the interior V-shaped groove 631 that impact block 63 inner rings initiatively are used to accommodate spin 67.Initiatively radial symmetric convexes with a pair of first end tooth 633 on the front end face of impact block 63.Between impact spring 65 and active impact block 63, be provided with packing ring and pad.Initiatively the front end of impact block 63 also is provided with passive impact block 69, and the protrusion of radial symmetric is provided with a pair of second end tooth 693 on the relative rear end face of passive impact block 69 and impact block initiatively 63.Power output system also comprises and extends gear-box 31 front ends, is connected in the working shaft 691 of passive impact block 69.Working shaft 691 front ends are provided with accepting groove 695, can when realizing difference in functionality, accommodate the corresponding work head, and clamp fixing through chuck 9.Chuck 9 is set in working shaft 691 front ends.
Multi-functional brill 1 of the present invention also has torsion control system, is used for adjustable max. output torque that power output system is set when the screwdriver function.Torsion control system below is detailed.
Referring to Fig. 3, Fig. 4, Fig. 5, Fig. 6, Fig. 7, Fig. 9, torsion control system comprises torsion cover 13, spiral cover 71, torque spring 73, quiet end tooth 75, moved end tooth 77.
Through the adjusting of function switched system, many merits of present embodiment are bored 1 and optional are had an impact wrench function, the high speed drill function, and low speed bores function, screwdriver function.The function switched system of present embodiment below is detailed.
Referring to Fig. 3, Fig. 4, Fig. 5, Fig. 6, the function switched system mainly comprises function switching button 17, switches ring 81, switches spring 171, fore-set 173, impact wrench switch piece 83, speed switch piece 85, screwdriver switch piece 87, clutch part 89.
Function switching button 17 comprises toggle that is arranged in switching window 19 and the housing that extend into the semi-round ring shape of housing 3; The housing of function switching button 17 is arranged with and switches ring 81; Switch ring 81 and be sleeved on the back cover 35, and can be driven with respect to back cover 35 around axis 10 rotations by function switching button 17.Have a breach on the anchor ring of switching ring 81, switching spring 171 and fore-set 173 pass this breach and are arranged between function switching button 17 and the back cover 35.Back cover 35 is provided with four recess that distribute along circumferentially, aforesaid four predeterminated position correspondences of these four recess and function switching button 17, and when fore-set 173 stayed in a recess, function switching button 17 stayed in a function corresponding gear.Be that the operator can stir function switching button 17 and circumferentially moves; Drive switching ring 81 through fore-set 173 and rotate, when moving to recess, switch spring 171 compressing fore-sets, 173 entering recess and tend to stay in this recess; This knee springing of operator's perception and know and got into a function gear; When needs change function, the elastic force drive fore-set 173 that the operator overcomes switching spring 171 leaves this another recess that needs of recess entering, and the drive switching encircles 81 rotations accordingly.
Impact wrench switches groove 811 and is the tortuous shape with ladder, is parallel to each other spaced apart in the axial direction straight trough and the composition of the link slot between two sections straight troughs by two sections.This two ends straight trough is perpendicular to axis 10.Impact wrench switch piece 83 housings can move axially and rotatable into strips.The one of which end is provided with pin, and pin is arranged in impact wrench and switches groove 811, and through the fit structure of this pin and groove, when switching ring 81 and rotating, pin switches in the groove 811 at impact wrench and moves to another section straight trough from one section straight trough, and drive impact wrench switch piece 83 moves axially.
The other end of impact wrench switch piece 83 is bent to form to the radially inner side of gear-box 13 and colludes, and colludes in the annular groove 891 that extend on the clutch part 89.Clutch part 89 is sleeved on outside second planet carrier 47, housing circlewise, annular groove 891 is positioned on its outer peripheral face.The inner peripheral surface of clutch part 89 is provided with slide block 893, and front end face is provided with clutch block 895.The outer peripheral face of second planet carrier 47 is provided with the slide rail 473 that matches with slide block 893, clutch part 89 thereby follow the rotation of second planet carrier 47 all the time, and can move axially by relative second planet carrier 47.Initiatively the rear end face of impact block 63 is provided with the clutch slot 635 that matches with clutch block 895.Through aforesaid structure, front position on clutch part 89 has axially and position, back, clutch block 895 blocks clutch slot 635 in the front position, and clutch block 895 breaks away from clutch slot 635 in the position, back.Through switching ring 81, impact wrench switch piece 83 drives between front position and position, back and moves clutch part 89 by function switching button 17.
Similarly, speed is switched groove 813 and is the tortuous shape with ladder, is parallel to each other spaced apart in the axial direction straight trough and the composition of the link slot between two sections straight troughs by two sections.This two ends straight trough is perpendicular to axis 10.Speed switch piece 85 housings can move axially and rotatable into strips.The one of which end is provided with pin, and pin is positioned at speed and switches groove 813, and through the fit structure of this pin and groove, when switching ring 81 and rotating, pin switches in the groove 813 in speed and moves to another section straight trough from one section straight trough, and drive speed switch piece 85 moves axially.
The other end of speed switch piece 85 is bent to form to the radially inner side of gear-box 13 and colludes, and colludes in the annular groove 533 of the outer peripheral face that extend into second ring gear 53.Also be provided with spline 531 on the front end face of second ring gear 53, the internal spline 775 of this spline 531 and moved end tooth 77 matches.Foregoing, second ring gear 53 has front position and position, back, corresponding respectively two kinds of speed output.Cooperate above-mentioned structure, through switching ring 81, speed switch piece 85 drives between front position and position, back and moves second clutch part 53 by function switching button 17.
Screwdriver switches groove 815 for for to have the irregularly shaped of ladder, upwards has wide and narrow portion week, and narrow front end is back in the axial direction in wide front end.Has transition portion between wide and narrow.Screwdriver switch piece 87 is in strip, and can move axially and rotatable.One end has the pin that is arranged in screwdriver switching groove 815, also is provided with spring 871 between this end and the gear-box, and this spring 871 orders about screwdriver switch piece 87 front end of butt screwdriver switching groove 813 forward.The keyway 771 of the other end of screwdriver switch piece 87 and moved end tooth 77 matches.Through this pin and the fit structure of groove, when switching ring 81 and rotating, pin switches in the groove 815 wide at screwdriver and moves to narrow or from narrow mobile wide portion, drive screwdriver switch piece 85 moves axially.Screwdriver switch piece 85 thus have axially on front position and position, back, the keyway 771 of the end of screwdriver switch piece 85 engagement moved end tooth 77 when the front position, the end of screwdriver switch piece 85 breaks away from the keyway 771 of moved end tooth 77 when the position, back.Through this mode rotatablely moving of locking moved end tooth 77 optionally.
The function handoff procedure of multi-functional brill 1 below is detailed.
Foregoing, multi-functional brill 1 can be in the impact wrench function, the high speed drill function, and low speed bores function, switches forward or backwards successively between the screwdriver function.The conversion of these functions and second ring gear 53; The front and back position of clutch part 89 and screwdriver switch piece 87 is closely related; Table one is illustrated in the aforesaid four kinds of functional statuses and second ring gear 53, the corresponding relation of clutch part 89 and screwdriver switch piece 87 position separately.
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| The impact wrench function | Back position | Back position | The front position |
| The high speed drill function | Back position | The front position | The front position |
| Low speed bores function | The front position | The front position | The front position |
| The screwdriver function | The front position | The front position | Back position |
Table one
With the impact wrench function is original state, like Figure 10, and Figure 11, function switching button 17 is in the impact wrench gear, and second ring gear 53 is positioned at the position, back, and clutch part 89 is positioned at the position, back, and screwdriver switch piece 87 is positioned at the front position.
Foregoing, when second ring gear 53 is positioned at the position, back, mesh the sun gear 45 and second planetary gear 49 simultaneously, planetary gear reduction system is exported high rotating speed to power output system.And the internal spline 775 of the spline 531 of second ring gear 53 and moved end tooth 77 breaks away from each other at this moment, and second ring gear 5 can be by sun gear 45 driven rotary.Screwdriver switch piece 87 is in the front position at this moment, and its end snaps in the keyway 771 of moved end tooth 77, forbids that moved end tooth 77 rotates.Yet therefore be provided with screwdriver switch piece 87 to such an extent that under this functional status be in back position also be fine because moved end tooth 77 does not work this moment, can not influence the realization of impact wrench function.
When realizing the impact wrench function; Rotatablely move and output to main shaft 61 via second planet carrier 47; Because the pressure of impact spring 65, initiatively impact block 63 drives through the spin 67 that is sandwiched in interior V-shaped groove, outer V-shaped groove 611, follows main shaft 61 and rotates; Passive impact block 69 also rotates thereupon, drives working head (not shown) through working shaft 691 with chuck 9 and rapidly nut (not shown) is tightened.
After nut end face and workpiece (not shown) face contacted, the moment of resistance increased sharply, reach certain value after; Intermeshing active impact block 63 all is obstructed with passive impact block 69; Passive impact block 69 stops operating, but main shaft 61 still rotates under the driving of motor output shaft, forces spin 67 to overcome it and moves along trough roller with the frictional force between interior V-shaped groove, the outer V-shaped groove 611; Impact block 63 rearward moves thereby promote initiatively, and impact spring 65 is compressed.Thus, active impact block 63 is in the axial direction gradually away from passive impact block 69.After active impact block 63 moves axially the tooth depth apart from second end tooth 693 that just surpasses passive impact block 69; I.e. initiatively impact block 63 and 69 out-of-gear moments of passive impact block, main shaft 61 drive just initiatively that impact block 63 rotates, and make its first end tooth 633 slip over second end tooth 693 of passive impact block 69; Slipping over moment; Because the effect of impact spring 65, spin 67 are got back to original position along interior V-shaped groove, outer V-shaped groove 611 again, initiatively impact block 63 is pushed away forward; Impact second end tooth 693 of passive impact block 69 simultaneously along with main shaft 61 acceleration rotations; Make passive impact block 69 on direction of rotation, continue motion, so move in circles, screw element is tightened under impact moment.
During above-mentioned realization impact wrench function; Need the initiatively passive impact block 69 of impact block 63 rotary impacts at intermittence; Thereby make the working head (fastener head) can fastening nut, but realizing creeping into function, promptly during high speed drill function and low speed brill function; Only need working head (fluted drill) to continue to creep into, and no longer need the initiatively intermittence impact of impact block 31.Below detail and switch to the process of high speed drill function and the duty of high speed drill function from the impact wrench function.
With reference to Figure 10; Figure 11 and Figure 12, shown in Figure 13, when the impact wrench function switches to the high speed drill function; Switch ring 81 and rotate 811 displacements of drive impact wrench switching groove; The pin of impact wrench switch piece 83 is moved to another straight trough from a straight trough, thereby drive impact wrench switch piece 83 and move axially, and then drive clutch part 89 and move to the front position from the position, back.After accomplishing switching, second ring gear 53 is positioned at the position, back, and clutch part 89 is positioned at the front position, and screwdriver switch piece 87 is positioned at the front position.
Because therefore be provided with screwdriver switch piece 87 to such an extent that under this functional status be in back position also be fine because moved end tooth 77 does not work this moment, can not influence the realization of high speed drill function.
Foregoing; After clutch part 89 is positioned at the front position; 895 engagements of its clutch block are the clutch slot 635 of impact blocks 63 initiatively, and the transfer route of rotation output becomes by second planetary gear 47 and/or main shaft 63 to clutch part 89 to active impact block 63, is delivered to working shaft 691 through passive impact block 69 again.Concrete, in drilling process, because the moment of resistance that working shaft 691 receives increases gradually, initiatively 63 of impact blocks tend to towards motor 11 motions.At this moment; Because clutch part 89 has limited the moving backward in the axial direction of impact block 63 initiatively; First end tooth 633 of impact block 63, second end tooth 693 of passive impact block 69 of fitting all the time initiatively, simultaneously, initiatively impact block 63, passive impact block 69, working shaft 691 motion together on direction of rotation.Because passive impact block 69 can't break away from active impact block 63 all the time, promptly can't form impact between the two, continues to creep into so can guarantee working head.
In the above-mentioned embodiment; The particularly important is: when realizing that high speed drill or low speed bore function; Rotation process by motor 21 outputs is slowed down; Arriving the output 22 of deceleration system, be that middleware is delivered to initiatively impact block 63 with clutch part 89 then, is rigidly connected in other words to the fixed connection of impact block 63 initiatively with this output of having set up deceleration system and rotates with transmission; Because the output of main shaft 61 and deceleration system is fixed together through interference fit, also we can say and set up being fixedly connected of main shaft 61 and active impact block 63.And power tool is in the past being switched to by the impact wrench function when creeping into function, all be still rely on main shaft 61 and initiatively the flexible connection of the groove between the impact block 63 and ball system transmit and rotate.
Industry average technical staff expect easily, and clutch part 89 also can be selected to be set directly on the outer peripheral face of main shaft 61, along the setting of the axial direction slip of main shaft 61.In this embodiment; Clutch part 89 parts and main shaft 61 relatively-stationary linking to each other on direction of rotation; A part of selectable and initiatively impact block 63 engagements or disengaging through spline fitted; Under drill mode (comprising that high speed drill function and low speed bore function), set up main shaft 61 to being fixedly connected of active impact block 63 with this, the thinking of this embodiment is identical with aforesaid the preferred embodiments of the present invention, and its concrete form repeats no more.
Expect equally easily; Clutch part 89 can also be fixedly connected with active impact block 63 so that the form that is different from spline fitted is selectable; Also can adopt the form and second planet carrier 47 or the main shaft 61 relatively-stationary cooperation in rotation that are different from the slide block slide rail, for example, adopt buckle and hole to cooperate; Perhaps projection and groove fit realize clutch part 89 and initiatively optional being solidly connected of impact block 63, adopt the cooperation of spline fitted realization clutch part 89 and second planet carrier 47 or main shaft 61 etc.
Below introduce the switching of brill function and the concrete mode of action that low speed bores function from the high speed drill function to low speed.
Like Figure 12, Figure 13 and Figure 14, Figure 15.When the high speed drill function switches to low speed and bores function; Switch ring 81 and rotate 813 displacements of drive speed switching groove; The pin of speed switch piece 85 is moved to another straight trough from a straight trough; Thereby drive speed switch piece 85 and move axially, and then drive second ring gear 53 and move to the front position from the position, back.After accomplishing switching, second ring gear 53 is positioned at the front position, and clutch part 89 is positioned at the front position, and screwdriver switch piece 87 is positioned at the front position.
Foregoing, after second ring gear 53 moved to the front position from the position, back, the engagement of disengaging and sun gear 45 was still with 49 engagements of second planetary gear.Simultaneously; The spline 531 of second ring gear 53 and 775 engagements of the internal spline of moved end tooth 77; And screwdriver switch piece 87 is positioned at the front position at this moment; The end of screwdriver switch piece 87 snaps in the keyway 771 of moved end tooth 775, and moved end tooth 775 can not be rotatablely moved, and then second ring gear 53 can not be rotatablely moved.
Through above-mentioned fit system; Multi-functional brill 1 is positioned at low speed and bores under the function; Planetary gear reduction system outputs to power output system via foregoing double reduction with lower rotating speed, and the operating mode of power output system is consistent during with the high speed drill function, repeats no more at this.
Below introduce from low speed and bore function to the switching of screwdriver function and the concrete mode of action of screwdriver function.
Like Figure 14, Figure 15 and Figure 16, Figure 17.Bore function when switching to the screwdriver function from low speed; Switch ring 81 and rotate 815 displacements of drive screwdriver switching groove; With the pin of screwdriver switch piece 87 leniently portion move to narrow portion, thereby drive screwdriver switch piece 87 and move axially and arrive the position, back, break away from and the engagement of moved end tooth 77.After accomplishing switching, second ring gear 53 is positioned at the front position, and clutch part 89 is positioned at the front position, and screwdriver switch piece 87 is positioned at the position, back.
Foregoing, spiral cover 71 is through protruded stigma 711, and torque spring 73 is oppressed the column 753 of quiet end tooth 75, and wherein protruded stigma 711, and torque spring 73 is provided with column 753 one to one.Quiet end tooth 75 thereby by elasticity compressing butt moved end tooth 77, concrete, the end tooth 753 of quiet end tooth 75 and the end tooth of moved end tooth 77 773 are oppressed to mesh together, thereby stops moved end tooth 77 to rotate.This moment, quiet end tooth 75 was elements that unique direct prevention moved end tooth 77 rotates because screwdriver switch piece 87 breaks away from and the engagement of moved end tooth 77.
When carrying out the work of screwing; The operator drives spiral cover 71 through torsion cover 13 and moves forward and backward the decrement of regulating torque spring 73; Promptly regulate quiet end tooth 75 and be applied to the elastic force on the moved end tooth 77, to set the max. output torque of multi-functional brill 1 under the screwdriver function.Be rotated further the max. output torque of the moment of torsion of needs when ordering about working shaft 691 greater than setting; Second ring gear, 53 drive moved end teeth 77 overcome the rotation of elasticity forces; The quiet end tooth 75 of the promotion that goes round and begins again axially moves forward, and end tooth 773 and end tooth 753 be slope climbing movement each other.Be that moved end tooth 77 can not stop the rotation of second ring gear 53 again, thereby the output of motor only drives second ring gear 53 and rotate freely, and can not drive 47 rotations of second planet carrier, will rotatablely move outputs to power output system.
Claims (8)
1. a power tool comprises: housing; Motor is arranged in housing, has the output shaft that rotation output is provided; Planetary gear reduction system; Institute's speed planetary gear deceleration system comprises sun gear, is engaged in the planetary gear of the output gear of sun gear, around the ring gear of said planetary gear; The primary importance and the second place on said ring gear has axially; Mesh said sun gear and said planetary gear simultaneously at said primary importance ring gear, mesh said planetary gear, break away from said sun gear at second place ring gear; It is characterized in that: said power tool also comprises the moved end tooth, and tooth engagement in when said ring gear is positioned at the second place and said moved end is upwards to lock in week each other; And the spline part of the motion that rotates in a circumferential direction of optional locking moved end tooth.
2. power tool according to claim 1; It is characterized in that: comprise tooth in abutting connection with said moved end; The quiet end tooth that axially-displaceable is moving, and towards said moved end the direction of tooth is oppressed the elastic component of quiet end tooth, be provided with the end tooth that matches separately on the end face that said quiet end tooth and moved end tooth lean.
3. power tool according to claim 1; It is characterized in that: comprise the torsion cover; Screw thread is coupled to the spiral cover in the torsion cover; Said elastic component is the torque spring that is connected in said spiral cover, and the said spiral cover of said torsion cover scalable moves axially to regulate the decrement of said torque spring.
4. power tool according to claim 1; It is characterized in that: comprise function switching button; Said function switching button drives said spline part and moves with the optional primary importance and the second place of being positioned at; The motion that rotates in a circumferential direction at said primary importance spline part locking moved end tooth allows the motion that rotates in a circumferential direction of moved end tooth at second place spline part.
5. power tool according to claim 4 is characterized in that: an end face of said moved end tooth is provided with a plurality of keyways of circumferential distribution, and said spline part can move axially with the optional primary importance and the second place of being positioned at.End at said primary importance spline part engages said keyway, breaks away from said keyway at the end of said second place spline part.
6. power tool according to claim 5; It is characterized in that: comprise and switch ring; Which is provided with screwdriver and switch groove; Said spline part is provided with and is arranged in the pin that said screwdriver switches groove, and said function switching button drives said switching ring and rotates to drive said bearing pin to moving, and the spline part is axially moved between the primary importance and the second place.
7. power tool according to claim 4 is characterized in that: said function switching button drives said ring gear and moves axially with the optional primary importance and the second place of being positioned at.
8. power tool according to claim 1 is characterized in that: in the second place of ring gear, said moved end tooth and said ring gear are through the spline structure engagement.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010239512.5A CN102335907B (en) | 2010-07-20 | 2010-07-20 | Power tool |
| PCT/CN2011/077395 WO2012010093A1 (en) | 2010-07-20 | 2011-07-20 | Power tool |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010239512.5A CN102335907B (en) | 2010-07-20 | 2010-07-20 | Power tool |
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| CN102335907A true CN102335907A (en) | 2012-02-01 |
| CN102335907B CN102335907B (en) | 2014-04-16 |
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| CN201010239512.5A Active CN102335907B (en) | 2010-07-20 | 2010-07-20 | Power tool |
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| CN105936020A (en) * | 2013-08-23 | 2016-09-14 | 苏州宝时得电动工具有限公司 | Power tool |
| CN106914847A (en) * | 2015-12-28 | 2017-07-04 | 南京德朔实业有限公司 | Torque output tool |
| CN107470677A (en) * | 2016-06-08 | 2017-12-15 | 南京德朔实业有限公司 | Torsion exports instrument |
| CN110815138A (en) * | 2018-08-10 | 2020-02-21 | 工机控股株式会社 | Electric tool |
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