CN201124364Y - Power tool - Google Patents
Power tool Download PDFInfo
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- CN201124364Y CN201124364Y CN 200720044481 CN200720044481U CN201124364Y CN 201124364 Y CN201124364 Y CN 201124364Y CN 200720044481 CN200720044481 CN 200720044481 CN 200720044481 U CN200720044481 U CN 200720044481U CN 201124364 Y CN201124364 Y CN 201124364Y
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- power tool
- tool according
- ring gear
- pressing element
- groove
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Abstract
The utility model provides a power tool which comprises a motor, a housing, a gear reducing mechanism which is driven by the motor and accommodated in the housing, a clutch mechanism which includes a pressing element and an elastic element, and a torsion regulating element. The gear reducing mechanism includes a rotatable ring gear accommodated in the housing, the ring gear is provided with at least one flute on the outer surface, the pressing element can be arranged in any flute movably, the elastic element can be radially deformed and arranged between the pressing element and the torsion regulating element, thereby regulating the elasticity of the elastic element via the torsion regulating element.
Description
Technical field
The utility model relates to a kind of power tool, as screwdriver, have screwdriver and creep into double mode electric drill, have screwdriver, creep into, impact the percussion drill of three kinds of patterns, the utility model especially relates to a kind of power tool that adopts clutch mechanism to control the output torque upper limit.
Background technology
U.S. Pat 6,523, a kind of electric drill with screwdriver pattern and drill mode is disclosed for 658B2 number, this electric drill comprises motor, this motor has an output shaft, front portion at motor is provided with gear reduction, and this gear reduction comprises the third-level planetary tooth, and the support planet tooth that the third-level planetary frame is used for rotating and three grades of ring gears mesh with the planet tooth respectively.Be passed to the main shaft that is connected with third level planet carrier again after the speed reduction of this gear reduction with motor output shaft.Clutch mechanism is located at the front portion of gear reduction, and this clutch mechanism comprises that regulating sleeve is used for regulating torque, steel column and helical spring.The rear end of this steel column compresses the leading section of third level ring gear, and helical spring compresses steel column backward.The front end edge of third level ring gear is circumferentially equally spaced to be provided with some projectioies, and each projection all comprises the pair of angled surface.Steel column is against living projection, thereby can prevent that the rotation of the 3rd ring gear from allowing motor to transfer a torque to main shaft.Can set helical spring pressure by rotary regulating sleeve, thereby set the upper limit of each torsion shelves.Torsion shelves in a certain setting, when output torque reaches predetermined value, steel column will get over the projection of third level ring gear end face, make clutch mechanism thread off, thereby third level ring gear begins idle running, moment of torsion just can not be passed to main shaft, can prevent that the screw transition from tightening and damage working surface this moment.The setting of this clutch comprises that steel column and spring all arrange along ring gear vertically.Thereby make that the axial length of whole electric drill can be long.
In order to overcome long this defective of the axial fuselage of above-mentioned electric drill, disclosed a kind of hand-held tool European patent EP 1391269B1 number, this instrument comprises a gear box structure, this gear box structure comprises one-level epicyclic gear stage at least, one clutch mechanism is connected with the ring gear of this epicyclic gear stage, this clutch mechanism comprises some steel balls, and some springs have the annular ring of inclined surface.Equally spacedly on the outer peripheral face of the ring gear of described epicyclic gear stage be provided with some grooves; wherein accommodate a steel ball respectively in the part groove; steel ball radially push down described groove; each groove part has two inclined planes; described spring is axial arranged; one end is connected with outside adjustable ring; the other end compresses annular ring; because annular ring has an inclined surface, so spring can a part be divided into radial load to the axial application of force of annular ring, thereby annular ring can compress steel ball in radial direction; it is non-rotatable so that the ring gear of described epicyclic gear stage is fixed; thereby the transmission moment of torsion when output torque reaches certain value, overcomes spring force; steel ball can get over the inclined plane of ring gear groove; clutch is threaded off, thereby output torque can not be passed to working head, to reach the effect of protection working face.The setting of this clutch that discloses in this piece European patent, its medi-spring is axial setting, but steel ball is stressed, comprise that it all is radially that steel ball is given the application of force direction of ring gear, and spring and steel ball all are the peripheries at ring gear, its space that axially needs overlaps with ring gear is most of, makes that the axial fuselage length of entire tool is shorter relatively so such clutch is arranged.
The utility model content
Technical problem to be solved in the utility model provides a kind of new-type clutch arrangement and makes that the fuselage axial dimension of power tool is shorter.
In order to address the above problem, the utility model provides a kind of power tool, comprising: motor; Housing; Be subjected to described motor driving and be contained in the interior gear reduction of described housing, described gear reduction comprises the rotatable ring gear that is contained in the described housing; Clutch mechanism, described clutch mechanism comprises pressing element and flexible member; The torsion regulating element; The outer surface of described ring gear is provided with at least one groove, described pressing element movably places described any groove, being located between pressing element and the torsion regulating element of described flexible member radially variable shape, make that the elastic force of flexible member can be changed by regulating the torsion regulating element.
In the power tool that the utility model disclosed, the strain of flexible member is radially, and this arrangement makes the fuselage axis of power tool to shorter, more compact structure.
Description of drawings
The partial cross section figure of the three function percussion drills that Fig. 1 is disclosed for the utility model first embodiment.
Fig. 2 is the explosive view of the gear reduction of the three function percussion drills that Fig. 1 disclosed.
Fig. 3 is the toggle of the three function percussion drills that Fig. 1 disclosed and the explosive view of back cover.
Fig. 4 A is the explosive view of the torque force adjusting mechanism of the three function percussion drills that Fig. 1 disclosed.
In the torque force adjusting mechanism that Fig. 4 B is disclosed for Fig. 4 A the stereogram seen from the another one angle of first plate washer.
Fig. 5 is the main shaft self-locking mechanism of the three function percussion drills that Fig. 1 disclosed and the explosive view of beater mechanism.
Fig. 6 is the drill switching mechanism of the three function percussion drills that Fig. 1 disclosed and the explosive view of fore shell.
Fig. 7 A is the partial cross section figure of three function percussion drills when the screwdriver pattern that Fig. 1 disclosed.
Fig. 7 B for three function percussion drills that Fig. 1 disclosed along C-C to sectional view.
Fig. 7 C for three function percussion drills that Fig. 1 disclosed along D-D to sectional view.
Fig. 8 A is the partial cross section figure of three function percussion drills when drill mode that Fig. 1 disclosed.
The three function percussion drills that Fig. 8 B is disclosed for Fig. 8 A along E-E to sectional view.
Fig. 9 A is the partial cross section figure of three function percussion drills when conflicting model that Fig. 1 disclosed.
The three function percussion drills that Fig. 9 B is disclosed for Fig. 9 A along F-F to sectional view.
The partial sectional view of the clutch mechanism of the three function percussion drills that Figure 10 is disclosed for the utility model second embodiment.
The partial cross section figure of the three function percussion drills that Figure 11 is disclosed for the utility model the 3rd embodiment.
Among the figure:
| 1. three |
3. |
5. |
| 7. |
8. |
9. |
| 11. |
13. first |
15. |
| 17. |
19. |
21. second |
| 23. |
25. |
27. the |
| 29. the third line star- |
31. the |
33. the third |
| 35. |
37. large- |
39,39 ', 39 " |
| 41. |
43. |
45. |
| 47. |
49. |
51. |
| 53. |
55. |
57. |
| 59. |
61. back cover rear |
63. |
| 65. accepting |
67. swallow-tail |
69. |
| 71. |
73. |
75. |
| 77. accepting |
79. clicking |
81. |
| 83. |
85. torque |
87. |
| 89. |
91. |
93. torsion |
| 95. arc convex | 97,97 " |
99,99 " first steel ball |
| 101,101 " |
103. |
105. groove |
| 107. first accepting |
109. accepting |
111. through |
| 113. second accepting |
115. arch thin-walled | 117. |
| 119. through |
121. shifting |
123. |
| 125. transfer |
127. |
129. groove |
| 131. |
133. |
135. |
| 137. |
139. |
141. the inner surface of fixed |
| 143. |
145. |
147. end face bearing |
| 149. drill switching mechanism | 151. |
153. |
| 155. |
157. drill switches |
158. |
| 158a. little head end | 159. slit | 161. groove |
| 163. the hole that diameter is less | 165. the hole that diameter is bigger | 167. |
| 169. |
99 '. |
98 ". wedged block |
| 98a. inclined-plane |
The specific embodiment
Referring to figs. 1 through Fig. 2, a kind of three function percussion drills 1, can be operated at screwdriver, creep into and impact one of three kinds of patterns and carry out work.This three functions percussion drill 1 comprises motor 3, and this motor 3 has a motor rotating output shaft 5, and this motor rotating output shaft 5 is used for rotatablely moving of motor 3 is passed to main shaft 7.The front end that main shaft 7 is positioned at percussion drill 1 is used to drive working head (not shown) work, and the rearward end of main shaft 7 is provided with external splines 8.Be provided with gear reduction 9 between motor 3 and main shaft 7, this reduction gear 9 is passed to main shaft 7 after being used for the high rotational speed of motor output shaft 5 reduced again.
With reference to Fig. 3, back cover 59 rear inner surface 61 are smooth surface, its internal diameter is slightly larger than the external diameter of first ring gear, 11 large-diameter portions 37, when first ring gear 11 places in the back cover 59, have certain interval between the outer surface of first ring gear, 11 large-diameter portions 37 and back cover 59 rear inner surface 61, thereby the ring gear 11 of winning can be rotated relative to back cover 59.Back cover 59 front inner surface are used for and are located at external splines 45 engagement on second ring gear, 19 forward outer surface along being circumferentially with a circle internal spline 63, when two spline engagement, second ring gear, 19 relative back covers 59 are non-rotatable, but 19 axially movable the placing in the back cover 59 of second ring gear.At the mid portion of back cover 59 along circumferentially being respectively equipped with three accepting grooves 65, in back cover 59 external rear face upper edges circumferentially symmetry be provided with two radially outward outstanding swallow-tail form fixture blocks 67, these two swallow-tail form fixture blocks 67 are used for fixing elasticity lug 69 respectively.
Toggle 71 is used for controlling described gear reduction 9, makes three function percussion drills 1 be in low or first gear and top gear respectively.Toggle 71 comprises plectrum 73 and steel wire 75.Plectrum 73 is clamped in the outside of back cover 59, plectrum 73 upper edges are circumferentially with three accepting grooves 77, these three accepting grooves 77 respectively be located at back cover 59 on three accepting grooves 65 corresponding, plectrum 73 mid portions are radially outward outstanding is provided with a clicking section 79, clicking section 79 is exposed to the outside of back cover 59, when needs carried out rate conversion, the operator only need promote clicking section 79 and get final product.Steel wire 75 is a C shape structure, wherein the pars intermedia of C shape is bent inwardly into a protuberance 81, the both ends correspondence of C shape be bent inwardly into two bent end 83, the middle protuberance 81 of steel wire and two bent end 83 are passed accepting groove 77 and 65 respectively, and place in the annular groove 43 on second ring gear, 19 external rear face, thereby make that second ring gear 19 also can and then move axially when the clicking section 79 on the axial promotion plectrum 73.Second ring gear 19 movably is placed in two positions, when primary importance, second ring gear 19 and 21 engagements of second planetary gear, the external splines 45 of second ring gear, 19 outer surfaces meshes with the internal spline 63 of back cover 59 front inner surface simultaneously, this moment, second planetary gearsets was in deceleration regime, and three function percussion drills 1 are in low or first gear.Promote the clicking section 79 on the plectrum 73 backward, this moment, second inner ring 19 was in the second place, second ring gear 19 and 21 engagements of second planetary gear, simultaneously with first planet carrier, 17 external rear face on external tooth 53 engagements, this moment, the external splines 45 of second ring gear, 19 outer surfaces was thrown off with the internal spline 63 of back cover 59 front inner surface, second planetary gearsets is in the state that only transmits moment of torsion and do not slow down, and this moment, three function percussion drills 1 were in top gear.
With reference to Fig. 4 A to 4B, three function percussion drills 1 further comprise a torque force adjusting mechanism 85, and this torque force adjusting mechanism 85 is used for setting different torque magnitude when the screwdriver pattern.This torque force adjusting mechanism 85 comprises that first plate washer 87 is installed on the leading section of motor 3, second plate washer 89 is installed on the minor diameter part 35 of first ring gear 11, clutch mechanism 91 axial immovable being held between first plate washer 87 and second plate washer 89, one torsion adjustable ring, 93 axial immovable being held between first plate washer 87 and second plate washer 89, this torsion adjustable ring 93 is sheathed on the rear portion of back cover 59 simultaneously.
In first embodiment of the present utility model, the groove 39 that first ring gear, 11 minor diameter parts are provided with is a kind of arc groove, each arc groove 39 comprises two sides, the side of this arc groove 39 is a kind of guiding inclined plane of arc, forms a kind of arc convex 95 between per two arc grooves 39.Described clutch mechanism 91 comprises helical spring 97, and helical spring 97 also can be replaced by other flexible member certainly.End at helical spring 97 close first ring gears 11 is connected with one first steel ball 99, this first steel ball 99 places in the described arc groove 39, be provided with one second steel ball 101 at helical spring 97 away from an end of first ring gear 11, this second steel ball 101 is connected with described torsion adjustable ring 93 and can moves along the inwall of described torsion adjustable ring 93.Two altogether of described clutch mechanisms 91, the axially minor diameter part that compresses first ring gear 11 35 of symmetry.The rear inner surface of described torsion adjustable ring 93 is provided with two identical shaped cam surfaces 103, two cam surfaces 103 become 180 degree phase difference settings along circumferential direction, cam surface 103 is radially to projecting inward, and along a direction, cam surface 103 radially increases gradually to projecting inward thickness.Be provided with some grooves 105 on the front inner surface of torsion adjustable ring 93, groove 105 cooperates with lug 69 on being immobilizated in back cover 59 rear portion swallow-tail form fixture blocks 67, thereby makes can produce the sound of " click clatter " when rotary torsion adjustable ring 93.
Described clutch mechanism 91 is held between first accepting groove 107 and second accepting groove 113, and first steel ball 99, helical spring 97 and second steel ball 101 are radially arranged, and its arragement direction is vertical substantially with the axis of first ring gear 11.First steel ball 99 compresses arc groove 39, the second steel balls 101 and props up cam surface 103, and can move relative to cam surface 103.Rotary torsion adjustable ring 93, when the direction that increases towards cam surface 103 thickness is rotated, second steel ball 101 can radially move inward, thereby compression spring 97, when the direction that reduces towards cam surface 103 thickness is rotated, second steel ball 101 can radially outwards move, thereby the decrement of spring 97 obtains certain release.
With reference to Fig. 5 to 6, the front end face of the third line star frame 33 is axially extended to be provided with four shifting blocks 121, these four shifting blocks 121 are along circumferentially uniformly-spaced being provided with, the inner surface of the third line star frame 33 is provided with four projectioies 123, each projection 123 is all radially inwardly outstanding, these four projectioies 123 circumferentially uniformly-spaced are provided with, and form certain clearance between per two projectioies 123.Three function percussion drills 1 comprise that further a main shaft self-locking mechanism and beater mechanism are installed on the front end of gear reduction 9 successively.Described main shaft self-locking mechanism comprises a transfer panel 125, the external rear face of this transfer panel 125 uniformly-spaced is provided with four projectioies 127, be formed with a groove 129 between per two projectioies 127, these four projectioies 127 are accommodated in respectively in the described gap, groove 129 is used for accommodating projection 123, the width of its protrusions 123 is smaller than the width of groove 129, the width of projection 127 is smaller than the width in above-mentioned gap, thereby make that when transfer panel 125 is installed on the third line star frame 33 transfer panel 125 is a bit of distance of the third line star frame 33 rotations relatively.Correspondingly with groove 129 be provided with four planes 131 on the forward outer surface of transfer panel 125, the inner surface of transfer panel 125 is provided with internal spline 133, external splines 8 engagements of this internal spline 133 and main shaft 7 rearward end.When transfer panel 125 is installed on the third line star frame 33, four shifting blocks 121 are arranged on transfer panel 125 forward outer surface, and each shifting block 121 is between two planes 131, four rollers 135 are installed on respectively between the shifting block 121, and be positioned on the described plane 131, described main shaft self-locking mechanism also comprises a fixed disk 137, and the outer surface of fixed disk 137 is provided with some protruding 139, and the inner surface 141 of fixed disk 137 is a smooth surface.During assembling, fixed disk 137 is sheathed on the shifting block 121, and these fixed disk 137 loose fits are on described shifting block 121, and described roller 135 is between the inner surface 141 and described plane 131 of fixed disk.
The beater mechanism of three function percussion drills 1 comprises quiet end tooth 143 and moved end tooth 145, and wherein quiet end tooth 143 is to be born by fixed disk 137, is formed at the front end face of fixed disk 137.Moved end tooth 145 compression fit and can be with main shaft 7 axially-movables on main shaft 7.147 loose fits of end face bearing are on moved end tooth 145.Three function percussion drills 1 also comprise drill switching mechanism 149, and the effect of this impact switching mechanism 149 is to make three function percussion drills 1 change between drill mode and conflicting model.Drill switching mechanism 149 comprises that 153, three pins 155 of 151, three helical springs of three sleeves and a drill switch ring 157.Pin 155 comprises that a stub end 158 and a microcephaly hold 158a.
The rear inner surface upper edge of fore shell 57 is circumferentially with some slits 159, and these some slits 159 are used for accommodating the external splines 49 on the outer surface of the 3rd ring gear 27, thereby make the 3rd ring gear 27 non-rotatable being installed in the fore shell 57.Front end at each slit 159 offers a groove 161 more shallow slightly than slit 159, and groove 161 is used for accommodating the projection 139 on fixed disk 137 outer surfaces, thereby makes fixed disk 137 be installed in the fore shell 57 by non-rotatable.On fore shell 57, be circumferentially with three through holes near the first half edge, each through hole all is to be made of a less hole 163 and the bigger hole 165 of diameter of diameter, the less hole 163 of diameter is communicated with fore shell 57 inner surfaces, the hole 165 that diameter is bigger is communicated with fore shell 57 outer surfaces, forms a step surface 167 in the junction in the bigger hole 165 of the less hole 163 of diameter and diameter.Described sleeve 151 places in the less hole of diameter 163, described helical spring 153 places in the bigger hole of diameter 165, one end of helical spring 153 props up step surface 167, the other end props up the stub end 158 of pin 155, pin 155 passes whole through hole, and the stub end 158 of pin 155 is exposed to the outer surface of fore shell 57.The inner surface that drill switches ring 157 is provided with the phase difference setting that becomes 120 degree angles between 169, three cam surfaces 169 of three cam surfaces respectively.Each cam surface 169 all is radially inwardly outstanding, and increases gradually towards a direction thickness.Drill switches the outside that ring 157 is set in fore shell 57, make the stub end 158 of each pin 155 prop up cam surface 169, when the rotation drill switches ring 157, during the direction rotation that thickens towards cam surface 169, can make helical spring 153 compress, pin 155 radially moves inward, when pin 155 moves to certain distance, the microcephaly of pin 155 holds 158a can touch the side of end face bearing 147, thereby prevents that main shaft 7 and moved end tooth 145 from axially moving backward.Otherwise, when the direction rotation drill switching that reduces towards cam surface 169 thickness encircles 157, can make helical spring 153 stretch out, pin 155 radially outward moves, when pin 155 moves a certain distance, the microcephaly of pin 155 holds 158a can leave the side of end face bearing 147, thereby makes main shaft 7 and moved end tooth 145 to move axially.
To 7B, is the state diagrams of three function percussion drills 1 when being located at the screwdriver pattern with reference to Fig. 7 A.At this moment, first steel ball 99 places in the arc groove 95 of first ring gear, 11 minor diameter parts 35, second steel ball 101 withstands the cam surface 103 on torsion adjustable ring 93 inner surfaces, because the power that compresses of helical spring 97, the ring gear 11 of winning is fixed by non-rotatable relative casing 59, thereby the rotation of motor 3 can drive main shaft 7 runnings by the transmission of gear reduction 9.When operator's tighten the screws, when screw is tightened, tighten if continue again, can make the load that puts on the main shaft 7 increase, thereby make that putting on being used on first ring gear 11 makes the compress power of the power of first ring gear, 11 rotations above helical spring 97, this moment, first steel ball 99 will get over the projection 95 on first ring gear, 11 minor diameter parts 35, thereby make ring gear 11 relative casing 59 rotations of winning, this moment, motor 3 rotations just can not drive main shaft 7 rotations again, main shaft 7 stops operating, and can prevent that screw is by overtighten and destruction work surface.
By rotary torsion adjustable ring 93, can be so that second steel ball 101 withstands the different-thickness place of cam surface 103 respectively.When second steel ball 101 withstands cam surface 103 thickness smaller parts, the decrement of helical spring 97 is less relatively, putting on the pressure that load value on the main shaft 7 relatively hour will overcome helical spring 97 makes the steel ball 99 of winning get over projection 95, and cause clutch mechanism 91 to be threaded off, thereby make the rotation of motor 3 no longer drive main shaft 7 rotations, can prevent that screw is by overtighten.When second steel ball 101 withstands cam surface 103 thicker parts, the decrement of helical spring 97 is relatively large, putting on the pressure that just can overcome helical spring 97 when load on the main shaft 7 will reach a relatively large value makes the steel ball 99 of winning get over projection 95, and cause clutch mechanism 91 to be threaded off, thereby make the rotation of motor 3 no longer drive main shaft 7 rotations, can prevent that screw is by overtighten.
With reference to Fig. 7 C, when the screwdriver pattern, the stub end 158 of pin 155 props up drill and switches the thicker place of ring 157 cam surfaces 169, this moment helical spring 153 decrement maximums, the microcephaly of pin 155 holds the contacts side surfaces of 158a and end face bearing 147, thereby prevent that main shaft 7 and moved end tooth 145 from axially moving backward, so moved end tooth 145 produces impact with quiet end tooth 143 with regard to not contacting, be simple screwdriver pattern this moment.
With reference to Fig. 8 A to 8B, rotary torsion adjustable ring 93, make three function percussion drills 1 be converted to drill mode by the screwdriver pattern, this moment, second steel ball 101 withstood cam surface 103 thickness thickness, it is maximum that the decrement of helical spring 97 reaches, even if the load that puts on the main shaft 7 reaches a very big value, also can not overcome the pressure of helical spring 97 and make the steel ball 99 of winning get over projection 95, first ring gear 11 is fixed by non-rotatable relative casing 59 all the time, thereby the rotation of motor 3 can drive main shaft 7 runnings by the transmission of gear reduction 9.With identical when the screwdriver pattern, the stub end 158 of pin 155 props up drill and switches the thicker place of ring 157 cam surfaces 169, this moment helical spring 153 decrement maximums, the little head end of pin 155 and the contacts side surfaces of end face bearing 147, thereby prevent that main shaft 7 and moved end tooth 145 from axially moving backward, so moved end tooth 145 produces impact with quiet end tooth 143 with regard to not contacting.
To 9B, the rotation drill switches ring 157 with reference to Fig. 9 A, makes three function percussion drills 1 be converted to conflicting model by drill mode, and identical during with drill mode, second steel ball 101 withstands cam surface 103 thickness thickness, and it is maximum that the decrement of helical spring 97 reaches.Different is with drill mode, drill switching ring 157 is rotated to and makes the stub end 158 of pin 155 prop up the less place of drill switching ring 157 cam surfaces, 169 thickness, this moment, spring 153 compressions were released, pin 155 radially outward moves, the microcephaly of pin 155 hold 158a no longer with the contacts side surfaces of end face bearing 147, thereby make main shaft 7 and moved end tooth 145 to move axially, in the course of work, moved end tooth 145 and quiet end tooth 143 cooperate can produce impact.
With reference to Figure 10, be second embodiment of the present utility model, basic identical with first embodiment, the groove that different is is located at the first ring gear minor diameter part is not an arc groove, but both sides are the groove 39 ' of the similar isosceles trapezoid in cross section on inclined-plane, simultaneously the steel ball among first embodiment also is to be that the steel column 99 ' of truncated cone replaces by end face, and the tilt angle alpha of groove 39 ' side and steel column 99 ' end slope angle beta are roughly the same.
With reference to Figure 11, be the 3rd embodiment of the present utility model, basic identical with first embodiment, different is groove 39 " be arranged on the axial end of first ring gear 11; first steel ball 99 " axially movable place described groove 39 " in; second steel ball 101 " and helical spring 97 " radially arrange; second steel ball 101 " an end prop up described torsion adjustable ring 93, the other end props up described helical spring 97 "; helical spring 97 " except that with a end that second steel ball is connected also have an end to be connected with a wedged block 98 "; described wedged block 98 " radially can move, wedged block 98 " be provided with an inclined-plane 98a; this wedged block 98 " prop up described first steel ball 99 by this inclined-plane 98a ", wedged block 98 " be held in described first plate washer 87 and described first steel ball 99 " thereby between make wedged block 98 " axially not removable.By rotating described torsion adjustable ring 93, described helical spring 97 " can produce elastic deformation in radial direction; thereby make wedged block 98 " radially move, thereby by being located at wedged block 98 " on inclined-plane 98a put on first steel ball 99 " on axial force can change.
Claims (19)
1. a power tool comprises: motor; Housing; Be subjected to described motor driving and be contained in the interior gear reduction of described housing, described gear reduction comprises the rotatable ring gear that is contained in the described housing; Clutch mechanism, described clutch mechanism comprises pressing element and flexible member; The torsion regulating element; It is characterized in that: the outer surface of described ring gear is provided with at least one groove, described pressing element movably places described any groove, being located between pressing element and the torsion regulating element of described flexible member radially variable shape, make that the elastic force of flexible member can be changed by regulating the torsion regulating element.
2. power tool according to claim 1 is characterized in that: described flexible member is a helical spring.
3. power tool according to claim 1 is characterized in that: described pressing element is a steel ball.
4. power tool according to claim 1 is characterized in that: described groove has at least one guiding inclined plane.
5. power tool according to claim 4 is characterized in that: described groove comprises two relative guiding inclined planes.
6. power tool according to claim 4 is characterized in that: described guiding inclined plane is a kind of arc inclined plane.
7. power tool according to claim 4, it is characterized in that: described pressing element comprises that first end is used for compressing ring gear and is used for being connected with flexible member with second end, first end of this pressing element has at least one inclined plane, this inclined plane and described guiding inclined plane adjacency, and can slide along described guiding inclined plane.
8. power tool according to claim 7 is characterized in that: the angle of inclination on the angle of inclination on the inclined plane of first end of pressing element and the guiding inclined plane of described groove is roughly the same.
9. power tool according to claim 7 is characterized in that: described pressing element is a steel column.
10. power tool according to claim 1 is characterized in that: the inwall of described torsion regulating element is provided with cam surface, and this cam surface is radially inwardly outstanding, and described flexible member also can move along described cam surface against described cam surface.
11. power tool according to claim 10 is characterized in that: described cam surface is provided with two along the inwall of torsion regulating element, and these two cam surfaces become 180 degree phase difference settings.
12. power tool according to claim 11 is characterized in that: described pressing element and flexible member have a pair of respectively, are symmetrical arranged along the ring gear diametric(al).
13. power tool according to claim 10 is characterized in that: be provided with between the cam surface on described flexible member and the torsion regulating element inwall and be connected steel ball, this connection steel ball can move along described cam surface.
14. power tool according to claim 1 is characterized in that: described groove is along circumferentially being arranged on the outer surface of ring gear, and described pressing element radially movably places described groove.
15. power tool according to claim 14 is characterized in that: described ring gear comprises minor diameter part and large-diameter portion, and described groove is located on the outer surface of minor diameter part, and the inner surface of large-diameter portion is provided with internal tooth to be connected with other parts of gear reduction.
16. power tool according to claim 14, it is characterized in that: an end of the contiguous ring gear of described flexible member is connected with pressing element and radially compresses this pressing element, and described flexible member is connected with described torsion regulating element away from an end of ring gear.
17. power tool according to claim 14, it is characterized in that: this power tool also comprises first plate washer and second baffle, described first barrier casing is located on the ring gear, one side of this first plate washer is provided with first accepting groove, second barrier casing is located on the motor, which is provided with second accepting groove, described pressing element and flexible member radially movably are contained between first and second accepting grooves, and described torsion regulating element is immovable being held between first and second plate washers axially.
18. power tool according to claim 1 is characterized in that: described groove is arranged on the axial end of ring gear, and described pressing element is axially movable places described groove.
19. power tool according to claim 18 is characterized in that: be provided with wedged block between described pressing element and flexible member, the wedge surface of described wedged block props up described pressing element.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200720044481 CN201124364Y (en) | 2007-10-01 | 2007-10-01 | Power tool |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200720044481 CN201124364Y (en) | 2007-10-01 | 2007-10-01 | Power tool |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201124364Y true CN201124364Y (en) | 2008-10-01 |
Family
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200720044481 Expired - Fee Related CN201124364Y (en) | 2007-10-01 | 2007-10-01 | Power tool |
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| Country | Link |
|---|---|
| CN (1) | CN201124364Y (en) |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN101758294B (en) * | 2008-12-25 | 2012-03-28 | 苏州宝时得电动工具有限公司 | Reciprocating saw |
| CN101396811B (en) * | 2007-09-28 | 2012-04-25 | 苏州宝时得电动工具有限公司 | Power tool |
| CN102528123A (en) * | 2010-12-30 | 2012-07-04 | 苏州宝时得电动工具有限公司 | Speed changing tool |
| CN102695588A (en) * | 2009-12-17 | 2012-09-26 | 日东精工株式会社 | Threaded fastener tightening and loosening device |
| CN103878730A (en) * | 2012-12-21 | 2014-06-25 | 苏州宝时得电动工具有限公司 | Electric drill with torsion adjusting function |
| CN103883682A (en) * | 2012-12-23 | 2014-06-25 | 陈驰川 | Speed-changing gear box with built-in clutch |
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| CN102528123A (en) * | 2010-12-30 | 2012-07-04 | 苏州宝时得电动工具有限公司 | Speed changing tool |
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| CN103878730B (en) * | 2012-12-21 | 2016-02-17 | 苏州宝时得电动工具有限公司 | There is the electric drill of torsion regulatory function |
| CN103878730A (en) * | 2012-12-21 | 2014-06-25 | 苏州宝时得电动工具有限公司 | Electric drill with torsion adjusting function |
| CN103883682A (en) * | 2012-12-23 | 2014-06-25 | 陈驰川 | Speed-changing gear box with built-in clutch |
| CN103883682B (en) * | 2012-12-23 | 2016-05-04 | 陈驰川 | Built-in clutch gear gearbox |
| CN105459034A (en) * | 2014-09-30 | 2016-04-06 | 日东工器株式会社 | Valve device and pneumatic tool having the valve device |
| CN104595856A (en) * | 2014-11-20 | 2015-05-06 | 重庆长安汽车股份有限公司 | Automobile lamp dimming mechanism |
| CN106914847A (en) * | 2015-12-28 | 2017-07-04 | 南京德朔实业有限公司 | Torque output tool |
| CN106914847B (en) * | 2015-12-28 | 2019-03-08 | 南京德朔实业有限公司 | Torque output tool |
| CN108340322A (en) * | 2017-01-22 | 2018-07-31 | 南京德朔实业有限公司 | Power tool |
| CN108544431A (en) * | 2018-04-08 | 2018-09-18 | 泉州齐美电子科技有限公司 | A kind of adjustable drilling machine of impingement rotating speed |
| CN108544431B (en) * | 2018-04-08 | 2020-12-15 | 惠安县螺阳邓先鹏建筑物清洁服务中心 | Impact type rotating speed adjustable drilling machine |
| CN108393545A (en) * | 2018-04-19 | 2018-08-14 | 山推工程机械股份有限公司 | The self-centering tooling of bull gear gear hobbing process |
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Legal Events
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| C14 | Grant of patent or utility model | ||
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| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20081001 Termination date: 20121001 |