CN102335907B - Power tool - Google Patents
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- CN102335907B CN102335907B CN201010239512.5A CN201010239512A CN102335907B CN 102335907 B CN102335907 B CN 102335907B CN 201010239512 A CN201010239512 A CN 201010239512A CN 102335907 B CN102335907 B CN 102335907B
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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 the ring gear of speed handoff functionality.
Background technology
Power tool, especially drill type electric tool have planetary gear reduction system conventionally, for tens thousand of high rotating speeds that turn that motor is directly exported, are reduced to the lower rotating speed that is applicable to carrying out driller's work.Planetary gear reduction system generally includes planet carrier, planetary gear, and sun gear, ring gear etc., between them, combination repeatedly reduces motor speed.
Power tool is towards miniaturization, and multifunctional direction develops, and drill type electric tool starts integrated, has existed and has had screwdriver function simultaneously on the market, 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, while carrying out high low speed switching, often need ring gear to move axially to change the meshing relation of itself and planetary gear sun gear, when carrying out the switching of screwdriver function, often need the rotation of locking or permission ring gear.Prior art needs two different ring gears carry out respectively two kinds of above-mentioned functions to switch, and two ring gears mean the further minimizing that is difficult to of number of elements, and function switching mechanism arranges difficulty.
Summary of the invention
The object of the invention is: a kind of simplification that has is provided, is easy to the power tool of the function converting system that regulates.
For achieving the above object, technical scheme of the present invention is: a kind of power tool, comprising: 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, be engaged in the planetary gear of the output gear of sun gear, ring gear around described planetary gear, primary importance and the second place of described ring gear on having axially, at described primary importance ring gear, mesh described sun gear and described planetary gear simultaneously, at second place ring gear, mesh described planetary gear, depart from described sun gear, described power tool also comprises moved end tooth, and tooth engagement in when described ring gear is positioned at the second place and described moved end is upwards mutually to lock in week; And the spline part that optionally locks the motion that rotates in a circumferential direction of moved end tooth.
Further, comprise that axially movable quiet end tooth, and the elastic component of oppressing quiet end tooth towards the direction of described moved end tooth, be provided with the end tooth matching on the end face that described quiet end tooth and moved end tooth lean separately in abutting connection with described moved end tooth.
Further, comprise torsion cover, screw thread is coupled to the spiral cover in torsion cover, and described elastic component is the torque spring that is connected in described spiral cover, and the adjustable described spiral cover of described torsion cover moves axially to regulate the decrement of described torque spring.
Further, comprise function switching button, described function switching button drives described spline part to move to be optionally positioned at primary importance and the second place, and the motion that rotates in a circumferential direction at described 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.
Further, an end face of described moved end tooth is provided with a plurality of keyways of circumferential distribution, and described spline part can move axially to be optionally positioned at primary importance and the second place.End at described primary importance spline part engages described keyway, at the end of described second place spline part, departs from described keyway.
Further, comprise and switch ring, which is provided with screwdriver and switch groove, described spline part is provided with and is arranged in the pin that described screwdriver switches groove, described function switching button drives described switching ring to rotate to drive described pin to move axially, and spline part is moved axially between primary importance and the second place.
Further, described function switching button drives described ring gear to move axially to be optionally positioned at primary importance and the second place.
Further, in the second place of ring gear, described moved end tooth and described ring gear mesh by spline structure.
Compared with prior art, power tool of the present invention, by the moved end tooth arranging and ring gear matches, has been simplified setting and the adjusting of ring gear.
Accompanying drawing explanation
Below in conjunction with accompanying drawing, the invention will be further described.
Fig. 1 is the multi-functional drill front view of the specific embodiment of the invention
Fig. 2 is the multi-functional drill top view of the specific embodiment of the invention.
Fig. 3 is the cutaway view of main apparent direction of the multi-functional drill of the specific embodiment of the invention.
Fig. 4 is the cutaway view of overlooking direction of the multi-functional drill of the specific embodiment of the invention.
Fig. 5 is the decomposing schematic representation of the multi-functional drill of the specific embodiment of the invention.
Fig. 6 is the gear-box stereogram of the multi-functional drill of the specific embodiment of the invention.
Fig. 7 is the second ring gear stereogram of the multi-functional drill of the specific embodiment of the invention.
Fig. 8 is that the multi-functional drill of the specific embodiment of the invention is about impact wrench switching part mechanism stereogram.
Fig. 9 is that the multi-functional drill of the specific embodiment of the invention is about screwdriver switching part mechanism stereogram.
Figure 10 is the switching ring schematic diagram of impact wrench function of the multi-functional drill of the specific embodiment of the invention.
Figure 11 is the vertical view cutaway drawing of impact wrench function of the multi-functional drill of the specific embodiment of the invention.
Figure 12 is the switching ring schematic diagram of high speed drill function of the multi-functional drill of the specific embodiment of the invention.
Figure 13 is the vertical view cutaway drawing of high speed drill function of the multi-functional drill of the specific embodiment of the invention.
Figure 14 is that the low speed of the multi-functional drill of the specific embodiment of the invention bores the switching ring schematic diagram of function.
Figure 15 is that the low speed of the multi-functional drill of the specific embodiment of the invention bores the vertical view cutaway drawing of function.
Figure 16 is the switching ring schematic diagram of screwdriver function of the multi-functional drill of the specific embodiment of the invention.
Figure 17 is that the master of screwdriver function of the multi-functional drill of the specific embodiment of the invention looks cutaway view.
1 multi-functional drill 39 bearing 71 spiral covers
3 housing 41 first planet carrier 711 protruded stigmas
5 handle 43 the first row star-wheel 73 torque springs
The quiet end tooth of 7 power brick 45 sun gear 75
9 chuck 47 second planet carrier 751 columns
10 axis 473 slide rail 753 end teeth
11 switch 49 second planetary gear 77 moved end teeth
13 torsion cover 51 first ring gear 771 keyways
15 commutation button 53 second ring gear 773 end teeth
17 function switching button 531 spline 775 internal splines
171 switch spring 533 annular grooves 81 switches ring
173 fore-set 61 main shaft 811 impact wrench switch groove
19 switch initiatively impact block 813 speed switching grooves of window 63
21 motor 633 first end tooth 815 screwdrivers switch groove
23 interior output shaft 635 clutch slot 83 impact wrench switch pieces
25 outer output shaft 65 impact spring 85 speed switch pieces
The outer V-shaped groove 87 screwdriver switch pieces of 251 support 611
253 axle sleeve 67 spin 871 springs
31 gear-box 691 working shaft 891 annular grooves
33 fore shell 693 second end tooth 893 slide blocks
35 back cover 695 accepting groove 895 clutch blocks
37 middle cover 70 bearings
The specific embodiment
Shown in Fig. 1 to 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 drill 1.Multi-functional drill 1 has impact wrench function, high speed drill function, and low speed bores function, 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 drill 1 is similar to pistol-shaped, comprises the housing 3 that is substantially tubular, with the handle 5 of housing 3 angled layouts, and dismountable power brick 7 that is arranged at handle 5 bottoms.Housing 3 has longitudinal axis 10.
The front end of housing 3 is provided with for clamping the chuck 9 of working head, for clamp respectively different working head (not shown) when this multi-functional drill 1 is realized difference in functionality, as clamped fastener head when realizing impact wrench function, when realizing high speed drill function or low speed brill function, clamp fluted drill.Chuck 9 outsides are provided with torsion cover 13, and torsion cover 13 can rotate to regulate around axis 10 max. output torque of the multi-functional drill 1 in screwdriver function.The upper part of handle 5 is provided with for opening and closing the switch 11 of multi-functional drill 1.The interface portion of handle 5 and housing 3 is also provided with commutation button 15.Multi-functional drill 1 has two commutation 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 being circumferentially furnished with successively four predeterminated positions by end to end.Function switching button 17 can move between these four predeterminated positions, successively multi-functional drill 1 is placed in to impact wrench function, high speed drill function, and low speed bores function, screwdriver function.Switch on 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 in detail the internal structure of multi-functional drill 1.
As Fig. 3, take the one end at housing 3 upper grip 9 places is front end, and the relative other end is rear end.The rear end of housing 3 contains power source, is specially a direct current generator 21.Motor 21 has output shaft and rotatablely moves with output.In this specific embodiment, output shaft comprises interior output shaft 23 and outer output shaft 25.Interior output shaft 23 is by motor 21 driven rotary, and outer output shaft 25 is sleeved on interior output shaft 23 by 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 and output gear, and axle bed is positioned at the rear portion of outer output shaft 25, is set on interior output shaft 23; Output gear is positioned at the front portion of outer output shaft 25, for the dynamic rotation of motor 21 being exported to by gear structure to the deceleration system of multi-functional drill 1.The length of axle bed and diameter are all greater than output gear.
Output shaft extend in 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 the first planet carrier 41, the first row star-wheel 43, sun gear 45, the second planet carriers 47, the second planetary gear 49, and two ring gears, be respectively the first ring gear 51 and the second ring gear 53.
The first planet carrier 41 comprises columniform pedestal and the circumferential evenly spaced a plurality of planetary gear fulcrums that are arranged on pedestal end face.
Pedestal center is through hole, and pedestal is installed and is supported on the axle bed of output shaft by this through hole.Between pedestal and axle bed, be also provided with support system, specifically comprise that one is enclosed within outside motor output shaft, step-like support 251, one are arranged on the axle sleeve 253 between support 251 and the through-hole wall of pedestal and are arranged on the rear end of pedestal and the pad 255 between gear-box inwall bottom.This support system so that the first planet carrier 41 can be good with respect to axle bed rotation.It should be noted that, in the present embodiment, the major part of the pedestal of the first planet carrier is supported on axle bed, and the length of this axle bed is longer, the length that the supported parts of the first planet carrier 41 effectively support is longer, this can stablize the first planet carrier 41, and high-speed rotary transfers can significantly not wear and tear or lose efficacy for a long time.
Planetary gear fulcrum stretches out from the front end of pedestal, and a first row star-wheel 43 is installed on each planetary gear fulcrum.What in this specific embodiment, the number of planetary gear fulcrum and planetary gear 43 was corresponding is 3.The first row star-wheel 43 and output gear engagement, rotated around planetary gear fulcrum by its drive.The internal tooth engagement of 43 whiles of the first row star-wheel and the first ring gear 51.The first ring gear 51 is fixedly installed with respect to gear-box 31.
Planetary gear prop up the tip of the axis reach the first row star-wheel 43 before.Sun gear 45 comprises toothed disc and gear shaft.On the side face of toothed disc and gear shaft, be equipped with tooth.On toothed disc, have plurality of holes, the position of its position and quantity and planetary gear fulcrum and quantity are corresponding, so that sun gear 45 is installed to planetary gear, prop up the tip of the axis.Gear shaft around around be furnished with a plurality of the second planetary gears 49 with gear shaft engagement.The concrete quantity of the second planetary gear 49 is 5, is sleeved on one by one on the planetary gear fulcrum of respective amount of the second planet carrier 47.The second planet carrier 47 is fixedly connected with power output system.
The outside that the footpath of sun gear 45 and the second planetary gear 49 makes progress is provided with the second ring gear 53.And the end tooth of sun gear 45 and the second planetary gear 49 all can be engaged in the internal tooth of the second ring gear 53.The second ring gear 53 can move forward and backward with respect to gear-box 31 in the axial direction, has position after a front position and.In front position, the second ring gear 53 and the second planetary gear 49 engagements, and depart from sun gear 45; And the second ring gear 53 can not rotate in front position, week is upwards fixed with respect to gear-box.In rear position, the second ring gear meshes the end tooth of the gear ring of the second planetary gear 49 and sun gear 45 simultaneously; And rear position the second ring gear can be around axis 10 rotations, and week is upwards movable with respect to gear-box.
Introduce in detail the moderating process of planetary gear reduction system below.
Referring to 3, Fig. 4, Fig. 5, Fig. 6, Fig. 9, the output shaft rotation of motor 21, drives the first row star-wheel 43 star-wheel fulcrum rotation of detouring, and the internal tooth of the first row star-wheel 43 ring-types along the first ring gear 51 is creeped simultaneously, around axis 10 revolution.The revolution of the first row star-wheel 43 drives the first planet carrier 41 around axis 10 rotations.Sun gear 45 is connected with the first planet carrier 41 by three planetary gear fulcrums, thereby rotation together with the first planet carrier 41.Be more than the first order moderating process of planetary gear reduction system.In this process, the High Rotation Speed of output shaft output is by the preliminary reduction of the first row star-wheel 43, its speed reducing ratio is the inverse ratio of the number of teeth of output gear and the number of teeth of the first row star-wheel 43 of output shaft, and in the present embodiment, the gear ratio of output gear and the first row star-wheel 43 is 7:18.In order to reach the effect of preferably slowing down, this gear ratio preferably should be less than 1:2.The rotating speed that less gear ratio has reduced the first row star-wheel 43 is set, further improved the stability of deceleration system, simultaneously, be provided with longer axle bed and not only improved the stability supporting, also make the first row star-wheel 43 be arranged on position more forward in gear-box 31, forward position is than the bottom of gear-box, the space that footpath makes progress is larger, this also makes larger the first row star-wheel 43 is set, and then more tooth is set, and the less gear ratio of final acquisition becomes possibility.In this process, the first row star-wheel 43, around axis 10 revolution, drives the first planet carrier 41 and sun gear 45 rotations to reduce for the second time the rotation output speed to power output system.
Rotatablely move and output to after sun gear 45, according to former and later two positions of the second ring gear 53, to there being two kinds of deceleration situations.When the second ring gear 53 is positioned at front position, the second ring gear 53 does not optionally rotate and departs from sun gear, thereby the gear shaft of sun gear 45 drives the second planetary gear 49 around the planetary gear fulcrum rotation of the second planet carrier 47, and creep on the internal tooth of the second ring gear 53, around axis 10 revolution, and then drive the second planet carrier 47 around axis 10 rotations, will rotatablely move and be delivered to power output system.This process has formed the second level deceleration of planetary gear reduction system.When the second ring gear 53 is positioned at rear position, the second ring gear 53 is rotatable and mesh toothed disc and second planetary gear 49 of sun gear 45 simultaneously.Therefore, the rotation of sun gear 45 is delivered to the second planetary gear 49 and the second planet carrier 47 by the second ring gear 53, slows down and be cancelled in the second level.
To sum up, the planetary gear reduction system of the present embodiment can be exported two kinds of different rotating speeds.Yet it is possible that this planetary gear reduction system is improved to the rotating speed output that makes it to provide how different.For example, the first ring gear 51 is arranged to have and the second ring gear 53 He Hou positions, similar front position, make it can optionally mesh the first row star-wheel 43 and sun gear 45 simultaneously, or only mesh the first row star-wheel 43, then combine the front and back position relation of the first ring gear 51 and the second ring gear 53, at least 3 kinds of rotating speed outputs can be provided, and the setting that it is concrete and combination are that those skilled in the art are easy to according to the thought of foregoing description design, and at this, are not repeating.
The bonding part of fore shell 33 and back cover 35 is also provided with middle cover 37, and middle cover 37 is divided into former and later two parts by gear-box 31, and rear section mainly holds planetary gear reduction system, and forward part is mainly held power output system.The interior ring of middle cover 37 is provided with bearing 39, and bearing 39 supports the second planet carrier 47.
The power output system of this specific embodiment is below described in detail in detail.
As Fig. 3, Fig. 4, Fig. 5, Fig. 7, Fig. 8, foregoing, the second planetary gear 47 is fixedly connected with power output system, concrete, and the second planet carrier 47 is fixedly connected with by interference fit with main shaft 61, and main shaft 61 is followed the second planet carrier 47 rotations all the time.
Power output system comprises that one is set in the active impact block 63 on main shaft 61, the spin V-shaped groove beater mechanism of being located at the impact spring 65 between active impact block 63 and the 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 V-shaped groove 611 interior rollings outside, be steel ball in the present embodiment, and be located at active impact block 63 inner rings for accommodating the interior V-shaped groove 631 of spin 67.Initiatively on the front end face of impact block 63, radial symmetric convexes with a pair of the first end tooth 633.Between impact spring 65 and active impact block 63, be provided with packing ring and pad.Initiatively the front end of impact block 63 is also provided with passive impact block 69, and on passive impact block 69 rear end face relative with active impact block 63, the protrusion of radial symmetric is provided with a pair of the second end tooth 693.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 corresponding working head, and clamp fixing by chuck 9.Chuck 9 is set in working shaft 691 front ends.
Multi-functional drill 1 of the present invention also has torsion control system, for adjustable max. output torque that power output system is set when the screwdriver function.Torsion control system is below described in detail in detail.
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.
By the adjusting of function switched system, many merits of the present embodiment are bored 1 and are optionally had impact wrench function, high speed drill function, and low speed bores function, screwdriver function.The function switched system of the present embodiment is below described in detail in detail.
Referring to Fig. 3, Fig. 4, Fig. 5, Fig. 6, 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 being arranged in and switches pulling out button and extending into the housing of the semicircle annular of housing 3 of window 19, the housing of function switching button 17 is arranged with and switches ring 81, switch ring 81 and be sleeved on back cover 35, and can be driven with respect to back cover 35 and rotate around axis 10 by function switching button 17.Switch on the anchor ring that encircles 81 and have a breach, switching spring 171 and fore-set 173 are arranged between function switching button 17 and back cover 35 through this breach.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 stays in a recess, function switching button 17 stays in a corresponding function gear.Be that operator can stir function switching button 17 and circumferentially moves, by fore-set 173, drive and switch ring 81 rotations, when moving to recess, switching spring 171 compressing fore-sets 173 enters recess and tends to stay in this recess, this knee springing of operator's perception and know and entered a function gear, when needs change function, operator overcomes the elastic force that switches spring 171 and drives fore-set 173 to leave this recess to enter the recess that another needs, and drives and switch ring 81 and rotate accordingly.
It is the tortuous stepped shape of tool that impact wrench switches groove 811, be parallel to each other by two sections, and spaced apart in the axial direction straight trough and the composition of the link slot between two sections of straight troughs.This two ends straight trough is perpendicular to axis 10.Impact wrench switch piece 83 housings into strips, can move axially and not rotatable.Its one end is provided with pin, and pin is arranged in impact wrench and switches groove 811, and by the fit structure of this pin and groove, when switching ring 81 rotates, pin switches in groove 811 and moves to another section of straight trough from one section of straight trough at impact wrench, and drive impact wrench switch piece 83 moves axially.
The other end of impact wrench switch piece 83 is bent to form hook to the radially inner side of gear-box 13, hooks and extend in the annular groove 891 on clutch part 89.Clutch part 89 is sleeved on outside the second planet carrier 47, and circlewise, annular groove 891 is positioned on its outer peripheral face housing.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 the second planet carrier 47 is provided with the slide rail 473 matching with slide block 893, clutch part 89 thereby follow all the time the second planet carrier 47 rotation, and can move axially by relative the second planet carrier 47.Initiatively the rear end face of impact block 63 is provided with the clutch slot 635 matching with clutch block 895.By aforesaid structure, the front position He Hou position of clutch part 89 on having axially, blocks clutch slot 635 at front position clutch block 895, at rear position clutch block 895, departs from clutch slot 635.Clutch part 89 encircles 81 by function switching button 17 by switching, and impact wrench switch piece 83 drives and moves between He Hou position, front position.
Similarly, it be the tortuous stepped shape of tool that speed is switched groove 813, be parallel to each other by two sections, and spaced apart in the axial direction straight trough and the composition of the link slot between two sections of straight troughs.This two ends straight trough is perpendicular to axis 10.Speed switch piece 85 housings into strips, can move axially and not rotatable.Its one end is provided with pin, and pin is positioned at speed and switches groove 813, and by the fit structure of this pin and groove, when switching ring 81 rotates, pin switches in groove 813 and moves to another section of straight trough from one section of straight trough in speed, and drive speed switch piece 85 moves axially.
The other end of speed switch piece 85 is bent to form hook to the radially inner side of gear-box 13, hooks in the annular groove 533 of the outer peripheral face that extend into the second ring gear 53.On the front end face of the second ring gear 53, be also provided with spline 531, the internal spline 775 of this spline 531 and moved end tooth 77 matches.Foregoing, the second ring gear 53 has He Hou position, front position, respectively corresponding two kinds of speed output.Coordinate above-mentioned structure, the second clutch part 53 encircles 81 by function switching button 17 by switching, and speed switch piece 85 drives and moves between He Hou position, front position.
Screwdriver switches groove 815 for stepped irregularly shaped for tool, upwards has wide portion and narrow portion week, the front end of narrow portion in the axial direction after in the front end of wide portion.Between wide portion and narrow portion, there is transition portion.Screwdriver switch piece 87 is in strip, and can move axially and not rotatable.One end has the pin that is arranged in screwdriver switching groove 815, is also provided with spring 871 between this end and 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.By the fit structure of this pin and groove, while switching ring 81 rotation, pin switches at screwdriver the wide portion that in groove 815, wide portion moves to narrow portion or moves from narrow portion, drives screwdriver switch piece 87 to move axially.Screwdriver switch piece 87 thus have axially on He Hou position, front position, the keyway 771 of the end of screwdriver switch piece 87 engagement moved end tooth 77 when front position, when rear position, the end of screwdriver switch piece 87 departs from the keyway 771 of moved end tooth 77.By which rotatablely moving of locking moved end tooth 77 optionally.
The function handoff procedure of multi-functional drill 1 is below described in detail in detail.
Foregoing, multi-functional drill 1 can be in impact wrench function, high speed drill function, and low speed bores function, between screwdriver function, switches forward or backwards successively.These merit transformations of energy and the 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 aforesaid four kinds of functional statuses and the second ring gear 53, the corresponding relation of clutch part 89 and screwdriver switch piece 87 position separately.
| ? | The |
|
|
| Impact wrench function | Rear position | Rear position | Front position |
| High speed drill function | Rear position | Front position | Front position |
| Low speed bores function | Front position | Front position | Front position |
| Screwdriver function | Front position | Front position | Rear position |
Table one
Take impact wrench function as original state, as Figure 10, Figure 11, function switching button 17 is in impact wrench gear, and the second ring gear 53 is positioned at rear position, and clutch part 89 is positioned at rear position, and screwdriver switch piece 87 is positioned at front position.
Foregoing, when the second ring gear 53 is positioned at rear position, mesh sun gear 45 and the second planetary gear 49 simultaneously, planetary gear reduction system is exported high rotating speed to power output system.And now the spline 531 of the second ring gear 53 and the internal spline 775 of moved end tooth 77 depart from each other, the second ring gear 5 can be by sun gear 45 driven rotary.Now screwdriver switch piece 87 is in front position, and its end snaps in the keyway 771 of moved end tooth 77, forbids that moved end tooth 77 rotates.Yet now because moved end tooth 77 does not work, therefore screwdriver switch piece 87 is arranged to such an extent that under this functional status, in rear position, be also fine, can not affect the realization of impact wrench function.
Under impact wrench function, clutch part 89 is in rear position, and the clutch block 895 of clutch part 89 departs from the initiatively clutch slot 635 of impact block 63.
When realizing impact wrench function, rotatablely move and output to main shaft 61 via the second planet carrier 47, pressure due to impact spring 65, initiatively impact block 63 drives by being sandwiched in the spin 67 of interior V-shaped groove, outer V-shaped groove 611, following main shaft 61 rotates, passive impact block 69 also rotates thereupon, by working shaft 691 and chuck 9, drives working head (not shown) rapidly nut (not shown) to be tightened.
After nut end face and workpiece (not shown) face contact, the moment of resistance increases sharply, reach after certain value, intermeshing active impact block 63 and passive impact block 69 are all obstructed, passive impact block 69 stops operating, but main shaft 61 still rotates under the driving of motor output shaft, and the frictional force that forces spin 67 to overcome between itself and interior V-shaped groove, outer V-shaped groove 611 is moving along trough roller, thereby promote initiatively impact block 63, rearward move, make impact spring 65 compressed.Thus, active impact block 63 is in the axial direction gradually away from passive impact block 69.When active impact block 63 moves axially after the tooth depth of firm the second end tooth 693 over passive impact block 69 of distance, i.e. initiatively impact block 63 and passive impact block 69 out-of-gear moment, main shaft 61 just drives initiatively impact block 63 rotations, make its first end tooth 633 slip over the second end tooth 693 of passive impact block 69, slipping over moment, effect due to impact spring 65, spin 67 is again along interior V-shaped groove, outer V-shaped groove 611 is got back to original position, initiatively impact block 63 is pushed away forward, along with accelerating to rotate, impacts by main shaft 61 the second end tooth 693 of passive impact block 69 simultaneously, make passive impact block 69 in direction of rotation, continue motion, so move in circles, screw element is tightened under impact moment.
Above-mentioned while realizing impact wrench function, need initiatively impact block 63 intermittent rotaries to impact passive impact block 69, thereby make the working head (fastener head) can fastening nut, but creep into function in realization, while being 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 of impact block 31 to impact.Below describe in detail from impact wrench function and be switched to the process of high speed drill function and the duty of high speed drill function.
With reference to Figure 10, Figure 11 and Figure 12, shown in Figure 13, while being switched to high speed drill function from impact wrench 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 to move axially, and then drive clutch part 89 to move to front position from rear position.Complete after switching, the second ring gear 53 is positioned at rear position, and clutch part 89 is positioned at front position, and screwdriver switch piece 87 is positioned at front position.
Due to now, because moved end tooth 77 does not work, therefore screwdriver switch piece 87 is arranged to such an extent that under this functional status, in rear position, be also fine, can not affect the realization of high speed drill function.
Foregoing, when clutch part 89 is positioned at behind 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 the second planetary gear 47 and/or main shaft 63 to clutch part 89 to active impact block 63, then is delivered to working shaft 691 through passive impact block 69.Concrete, in drilling process, the moment of resistance being subject to due to working shaft 691 increases gradually, and initiatively 63 of impact blocks tend to towards motor 21 motions.Now, because clutch part 89 has limited the moving backward in the axial direction of impact block 63 initiatively, the first end tooth 633 of impact block 63 the second end tooth 693 of passive impact block 69 of fitting all the time initiatively, meanwhile, initiatively impact block 63, passive impact block 69, working shaft 691 motion together in direction of rotation.Because passive impact block 69 and active impact block 63 cannot depart from all the time, cannot form impact between the two, so can guarantee that working head continues to creep into.
In above-mentioned embodiment, the particularly important is: when realizing high speed drill or low speed brill function, the rotation of being exported by motor 21 is through slowing down, arrive the output 22 of deceleration system, then the clutch part 89 of take is delivered to initiatively impact block 63 as middleware, and the output of having set up deceleration system with this is rigidly connected to transmit rotation in other words to being fixedly connected with of impact block 63 of active; Because the output of main shaft 61 and deceleration system is fixed together by interference fit, main shaft 61 and being fixedly connected with of impact block 63 have initiatively also been set up.And power tool is in the past being switched to by impact wrench function while creeping into function, be all still rely on main shaft 61 and initiatively the flexible connection of the groove between impact block 63 and ball system transmit rotation.
Industry average technical staff easily expect, 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 being connected in direction of rotation, a part meshes or departs from active impact block 63 by spline fitted is selectable, with this, under drill mode (comprising high speed drill function and low speed brill function), set up main shaft 61 being fixedly connected with to active impact block 63, the thinking of this embodiment is identical with aforesaid the preferred embodiments of the present invention, and its concrete form repeats no more.
Equally easily expect, clutch part 89 can also to be different from, the form of spline fitted is selectable to be fixedly connected with impact block 63 initiatively, also can adopt the form and the second planet carrier 47 or the main shaft 61 relatively-stationary cooperation in rotation that are different from slide block slide rail, for example, adopt buckle and hole to coordinate, or projection and groove fit realize being optionally solidly connected of clutch part 89 and active impact block 63, and employing spline fitted realizes the cooperation of clutch part 89 and the second planet carrier 47 or main shaft 61 etc.
Below introduce and from high speed drill function to low speed, bore the switching of function and the concrete mode of action that low speed bores function.
As Figure 12, Figure 13 and Figure 14, Figure 15.While being switched to low speed brill function from high speed drill 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 to move axially, and then drive the second ring gear 53 to move to front position from rear position.Complete after switching, the second ring gear 53 is positioned at front position, and clutch part 89 is positioned at front position, and screwdriver switch piece 87 is positioned at front position.
Foregoing, the second ring gear 53 moves to behind front position from rear position, and the engagement of disengaging and sun gear 45, still with the second planetary gear 49 engagements.Simultaneously, the spline 531 of the second ring gear 53 and 775 engagements of the internal spline of moved end tooth 77, and now screwdriver switch piece 87 is positioned at front position, the end of screwdriver switch piece 87 snaps in the keyway 771 of moved end tooth 775, moved end tooth 775 can not be rotatablely moved, and then the second ring gear 53 can not be rotatablely moved.
By above-mentioned fit system, multi-functional drill 1 is positioned at low speed and bores under function, planetary gear reduction system outputs to power output system via foregoing double reduction by lower rotating speed, and the operating mode of power output system is consistent during with high speed drill function, does not repeat them here.
Below introduce from low speed and bore function to the switching of screwdriver function and the concrete mode of action of screwdriver function.
As Figure 14, Figure 15 and Figure 16, Figure 17.While being switched to screwdriver function from low speed brill function, switch ring 81 and rotate 815 displacements of drive screwdriver switching groove, by the pin of screwdriver switch piece 87 leniently portion move to narrow portion, thereby position after driving screwdriver switch piece 87 to move axially to arrive, departs from and the engagement of moved end tooth 77.Complete after switching, the second ring gear 53 is positioned at front position, and clutch part 89 is positioned at front position, and screwdriver switch piece 87 is positioned at rear position.
Foregoing, spiral cover 71 is by 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 and column 753 arrange one to one.Quiet end tooth 75 thereby by elasticity compressing butt moved end tooth 77, concrete, the end tooth 753 of quiet the end tooth 75 and end tooth 773 of moved end tooth 77 is oppressed meshes together, thereby stop moved end tooth 77 to rotate.Now, because screwdriver switch piece 87 departs from and the engagement of moved end tooth 77, quiet end tooth 75 is elements that unique direct prevention moved end tooth 77 rotates.
When carrying out the work of screwing, operator drives spiral cover 71 to move forward and backward the decrement that regulates torque spring 73 by torsion cover 13, regulate quiet end tooth 75 to be applied to the elastic force on moved end tooth 77, to set the max. output torque of multi-functional drill 1 under screwdriver function.When ordering about working shaft 691, be rotated further the max. output torque that the moment of torsion needing is greater than setting, the second ring gear 53 drives moved end tooth 77 to overcome the rotation of elasticity oppressive force, the quiet end tooth 75 of promotion going round and beginning 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 second ring gear 53 rotation again, thereby the output of motor only drives the second ring gear 53 to rotate freely, and can not drive the second planet carrier 47 rotations, will rotatablely move and output to power output system.
Claims (8)
1. a power tool, comprising: housing; Motor, is arranged in housing, has the output shaft that rotation output is provided; Planetary gear reduction system, described planetary gear reduction system comprises sun gear, be engaged in the planetary gear of the output gear of sun gear, ring gear around described planetary gear, primary importance and the second place of described ring gear on having axially, at described primary importance ring gear, mesh described sun gear and described planetary gear simultaneously, at second place ring gear, mesh described planetary gear, depart from described sun gear, it is characterized in that: described power tool also comprises moved end tooth, tooth engagement in when described ring gear is positioned at the second place and described moved end is upwards mutually to lock in week; And the spline part that optionally locks the motion that rotates in a circumferential direction of moved end tooth.
2. power tool according to claim 1, it is characterized in that: comprise in abutting connection with described moved end tooth, axially movable quiet end tooth, and the elastic component of oppressing quiet end tooth towards the direction of described moved end tooth, be provided with the end tooth matching on the end face that described quiet end tooth and moved end tooth lean separately.
3. power tool according to claim 2, it is characterized in that: comprise torsion cover, screw thread is coupled to the spiral cover in torsion cover, described elastic component is the torque spring that is connected in described spiral cover, and the adjustable described spiral cover of described torsion cover moves axially to regulate the decrement of described torque spring.
4. power tool according to claim 1, it is characterized in that: comprise function switching button, described function switching button drives described spline part to move to be optionally positioned at primary importance and the second place, the motion that rotates in a circumferential direction at described 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, it is characterized in that: an end face of described moved end tooth is provided with a plurality of keyways of circumferential distribution, described spline part can move axially to be optionally positioned at primary importance and the second place, end at described primary importance spline part engages described keyway, at the end of described second place spline part, departs from described keyway.
6. power tool according to claim 5, it is characterized in that: comprise and switch ring, which is provided with screwdriver and switch groove, described spline part is provided with and is arranged in the pin that described screwdriver switches groove, described function switching button drives described switching ring to rotate to drive described pin to move axially, and spline part is moved axially between primary importance and the second place.
7. power tool according to claim 4, is characterized in that: described function switching button drives described ring gear to move axially to be optionally positioned at primary importance and the second place.
8. power tool according to claim 1, is characterized in that: in the second place of ring gear, described moved end tooth and described ring gear mesh by spline structure.
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 |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201010239512.5A CN102335907B (en) | 2010-07-20 | 2010-07-20 | Power tool |
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| CN102335907A CN102335907A (en) | 2012-02-01 |
| CN102335907B true 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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Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105904398B (en) * | 2013-08-23 | 2021-11-16 | 苏州宝时得电动工具有限公司 | Power tool |
| CN105459001A (en) * | 2015-12-17 | 2016-04-06 | 东莞市精心自动化设备科技有限公司 | Automatic screw locking device |
| CN205703930U (en) * | 2015-12-28 | 2016-11-23 | 南京德朔实业有限公司 | Torsion output instrument |
| CN107470677B (en) * | 2016-06-08 | 2019-11-22 | 南京德朔实业有限公司 | Torsion exports tool |
| CN110815138B (en) * | 2018-08-10 | 2024-02-02 | 工机控股株式会社 | Electric tool |
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| CN102335907A (en) | 2012-02-01 |
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