CN105333072B - torque output tool and transmission mechanism thereof - Google Patents
torque output tool and transmission mechanism thereof Download PDFInfo
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- CN105333072B CN105333072B CN201410308024.3A CN201410308024A CN105333072B CN 105333072 B CN105333072 B CN 105333072B CN 201410308024 A CN201410308024 A CN 201410308024A CN 105333072 B CN105333072 B CN 105333072B
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 87
- 230000007246 mechanism Effects 0.000 title claims abstract description 46
- 230000002093 peripheral effect Effects 0.000 abstract description 5
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- 230000007812 deficiency Effects 0.000 description 1
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Abstract
The invention discloses a transmission mechanism, comprising: the gearbox comprises a gearbox shell, a central transmission part, a main planet wheel carrier and a main gear ring which can move in the gearbox shell along the axial direction; the transmission mechanism further includes: first planetary gear set and second planetary gear set, first planetary gear set includes first kind of planet gear, and the second planetary gear set includes second kind of planet gear, and the sun-driven piece includes: a first central wheel portion, a first outer peripheral wheel portion; the main gear ring is provided with: can with the first ring gear portion of first kind of planetary gear meshing, can with the second ring gear portion of second kind of planetary gear meshing and first outer peripheral gear portion equal meshing, the main ring gear has in the axial: a first axial position at which the first ring gear portion is engaged with the first-type planetary gear, a second axial position at which the second ring gear portion is engaged with the second-type planetary gear, and a third position at which the second ring gear portion is engaged with both the second-type planetary gear and the first outer peripheral gear portion. The transmission of the present invention has a plurality of different transmission speed ratios.
Description
Technical field
The present invention relates to a kind of torque output instrument, and in particular to a kind of torque output instrument and its transmission mechanism.
Background technology
Existing electric tool, because small volume, lightweight, compact conformation, transmission efficiency, gearratio are big, transmission is flat
Surely, shock resistance and antivibration kinetic force are strong, therefore are commercially especially in great demand.
At present, electric tool generally only has a kind of speed output, and the requirement with people to electric tool performance is more next
It is higher, it is desirable to which that electric tool can have different transmission speed ratios according to actual needs.
The content of the invention
To solve the deficiencies in the prior art, it is an object of the invention to provide a kind of biography with multiple different transmission speed ratios
Motivation structure.
In order to realize above-mentioned target, the present invention is adopted the following technical scheme that：
A kind of transmission mechanism, including：Gear box casing, the central driving medium that can be pivoted by axle of first axle, primary planet
Wheel carrier, the main gear ring that can be axially moveable in gearhousing body；Transmission mechanism also includes：It is separately mounted to primary planet wheel carrier not
The first planetary gear set and the second planetary gear set at coaxial position, the first planetary gear set include more than two first kind planets
Gear, the second planetary gear set includes more than two Equations of The Second Kind planetary gears, and central driving medium includes：In the first planetary gear set
The first center wheel portion, the first periphery wheel portion engaged at the heart with first kind planetary gear, the first center wheel portion and the first periphery wheel
The periphery in portion is equipped with driving cog；Main gear ring at least provided with：The the first ring gear portion that can be engaged with first kind planetary gear, can be with
The second ring gear portion that two class planetary gears are engaged or can engaged with Equations of The Second Kind planetary gear and the first periphery wheel portion, main gear ring exists
At least have on axial direction：Make the first axial location that the first ring gear portion engages with first kind planetary gear, make the second ring gear portion only
The second axial location for being engaged with Equations of The Second Kind planetary gear, make the second ring gear portion and Equations of The Second Kind planetary gear and the first periphery wheel portion
The 3rd position engaged.
Further, the first planetary gear set is located at the front side of the second planetary gear set in the axial direction.
Further, the front end of primary planet wheel carrier is also formed with a second center wheel portion, the periphery of the second center wheel portion
Provided with driving cog.
Further, transmission mechanism also includes：One output shaft and an output end Gear Planet Transmission component, output end planet
Transmission component includes：Output end planetary gear that two or more is engaged with the second center wheel portion, output end planetary wheel carrier, one
Individual output end gear ring；Output end planetary wheel carrier is constituted with output shaft and is driven.
Further, first kind planetary gear and Equations of The Second Kind planetary gear are symmetrical arranged with respect to first axle.
Further, first kind planetary gear is identical with the planetary number of Equations of The Second Kind and in the circumference of primary planet wheel carrier
Upper correspond is set.
Further, the first kind planetary gear and Equations of The Second Kind positioned at the same circumferential position of primary planet wheel carrier are planetary
Take turns overlapping of axles.
Further, the planetary tooth radius of the first kind is less than the planetary tooth radius of Equations of The Second Kind.
Further, transmission mechanism also includes：More than two input planetary gears, input centre wheel, one
Individual input gear ring；Central driving medium rotates connection input planetary gear, and input planetary gear is nibbled with input centre wheel
Close.
The present invention also proposes a kind of torque output instrument, including：Instrument casing, motor, in addition to：Above-described transmission
Mechanism.
The present invention is advantageous in that：The transmission mechanism of the present invention is made by switching the axially different position of main gear ring
Obtaining transmission mechanism has different transmission speed ratios, and output shaft has different output speeds, solves existing transmission mechanism only
The problem of being exported with a kind of transmission of speed, meets demand of the people to drive mechanism performance.
Brief description of the drawings
Fig. 1 show the exploded perspective view of the transmission mechanism of the present invention；
Fig. 2 show the partial sectional schematic view of the transmission mechanism in Fig. 1, and now main gear ring is located at the first axial location；
Fig. 3 show the partial sectional schematic view of the transmission mechanism in Fig. 1, and now main gear ring is located at the second axial location；
Fig. 4 show the partial sectional schematic view of the transmission mechanism in Fig. 1, and now main gear ring is located at the 3rd axial location.
Embodiment
Make specific introduce to the present invention below in conjunction with the drawings and specific embodiments.
The present invention proposes a kind of transmission mechanism, and the transmission mechanism can be used in common torque output instrument, by this
Transmission mechanism can cause torque output instrument to have different operating rates, and can be under different operating rates freely.
Fig. 1 show the exploded perspective view of the transmission mechanism of the present invention.It refer to shown in Fig. 1, transmission mechanism of the invention
（Figure is not marked）Including：Gear box casing 100, output end Gear Planet Transmission component 200, output shaft 300, input Gear Planet Transmission component
400th, the first planetary gear set 500, the second planetary gear set 600, primary planet wheel carrier 700, central driving medium 800, main gear ring 900, its
Middle output shaft 300 is as the final torque output section of the transmission mechanism of the present invention, and it can surround the first axle Y where itself
Pivot.In the present invention, illustrate technical scheme in order to clearly convenient, especially make and being defined as below, this definition is not
It is used as the essentiality content of the limitation present invention：Direction where the first axle Y of output shaft 300 and parallel to first axle Y
Direction be defined as axial direction, be circumferential around axially direction, before the outbound course towards output shaft 300 is, towards output
After the direction opposite with outbound course of axle 300 is.
Fig. 2 show the partial sectional schematic view of the transmission mechanism in Fig. 1, and now main gear ring is located at the first axial location.
Please with reference to Fig. 1 and Fig. 2, gear box casing 100 for the transmission mechanism in the present invention shell, for housing input planet
Transmission component 400, the first planetary gear set 500, the second planetary gear set 600, primary planet wheel carrier 700, central driving medium 800, main tooth
Circle 900.Specifically, in the present embodiment, the inner circumferential of gear box casing 100 is provided with the internal spline that can coordinate with main gear ring 900
110。
Output end Gear Planet Transmission component 200 is used for torque drive to output shaft 300, and by output shaft 300 by moment of torsion
Export to workpiece to realize transmission agency.Output end Gear Planet Transmission component 200 includes：Output end planetary gear 210, output end row
Star wheel frame 220 and output end gear ring 230.In the present embodiment, with multiple output end planetary gears 210, the plurality of output
End planetary gear 210 is arranged at the rear side of output end planetary wheel carrier 220 and rotated with output end planetary wheel carrier 220 and is connected.Output
The rear side of planetary wheel carrier 220 is held to be provided with and the corresponding planet pin 221 of the number of output end planetary gear 210 and position, planet
Pin 221 is used to output end planetary gear 210 being arranged thereon, so that output end planetary wheel carrier 220 and output end planet tooth
Wheel 210 constitutes drive connection；Output end planetary wheel carrier 220 also passes through spline plectrum（Figure is not marked）It is connected with output shaft 300,
So as to output torque to output shaft 300.Output end gear ring 230 is sheathed on multiple outsides of output end planetary gear 210, its inner circumferential
Driving cog is provided with, so that cooperation is engaged with output end planetary gear 210, and output end ring gear opposed gear tank shell 100
Circumferential position is fixed.
Input Gear Planet Transmission component 400 includes：Input planetary gear 410, input centre wheel 420 and input end tooth
Circle 430.Input centre wheel 420 is used to extraneous moment of torsion introducing input Gear Planet Transmission component 400, and for example it can be with one
Motor is connected.Input planetary gear 410 include it is multiple, multiple input planetary gears 410 are arranged at input center
The periphery of wheel 420, and be driven and engage with it.Input gear ring 430 is sheathed on the outside of multiple input planetary gears 410, and
Constitute therewith and be additionally provided with peripheral structure 431 on engaged transmission, the periphery of input gear ring 430, caused by the peripheral structure 431
Input gear ring 430 is circumferentially fixed on gear box casing 100.
First planetary gear set 500, the second planetary gear set 600 are separately mounted to the different axial positions of primary planet wheel carrier 700
Put, and the first planetary gear set 500 is also located at the front side of the second planetary gear set 600 in the axial direction.Specifically, the first planetary gear set
500 include multiple first kind planetary gears 510, and the second planetary gear set 600 includes multiple Equations of The Second Kind planetary gears 610, primary planet
Wheel carrier 700 includes wheel carrier body 710, the center wheel portion 730 of trundle 720 and second.Trundle on primary planet wheel carrier 700
720 are used to install first kind planetary gear 510 and Equations of The Second Kind planetary gear 610, and the method that trundle 720 passes through interference fit
First kind planetary gear 510 and Equations of The Second Kind planetary gear 610 are fixedly mounted on primary planet wheel carrier 700, so that first
Class planetary gear 510, Equations of The Second Kind planetary gear 610 and primary planet wheel carrier 700 constitute synchronous axial system.Second center wheel portion 730
Positioned at the front end of primary planet wheel carrier 700, it is in the lump with the synchronous axial system of primary planet wheel carrier 700, the periphery of the second center wheel portion 730
The driving cog engaged with the output end planetary gear 210 in output end Gear Planet Transmission component 200 is additionally provided with, so that primary planet wheel carrier
700 can be by torque output to output end Gear Planet Transmission by the second center wheel portion 730 and engaging for output end planetary gear 210
Component 200.In the present embodiment, the first planetary gear set 500 includes three first kind planetary gears 510, three first kind planets
Gear 510 is symmetrical arranged with respect to first axle Y, and the second planetary gear set 600 includes three Equations of The Second Kind planetary gears 610, three the
Two class planetary gears 610 are also also symmetrical arranged with respect to first axle Y, and each Equations of The Second Kind planetary gear 610 is in primary planet wheel carrier 700
On circumferential position on primary planet wheel carrier 700 of circumferential position and first kind planetary gear 510 correspond, and circumferential position
Corresponding first kind planetary gear 510 and the wheel overlapping of axles of Equations of The Second Kind planetary gear 610, in the present embodiment, positioned at main row
The radius of the first kind planetary gear 510 of the front end of star wheel frame 700 is also less than the Equations of The Second Kind planet positioned at the rear end of primary planet wheel carrier 700
The radius of gear 610.
Central driving medium 800 is arranged at the front side of input Gear Planet Transmission component 400, and it can surround axially pivoting.Center
Driving member 800 includes：First center wheel portion 810 and the first periphery wheel portion 820.First periphery wheel portion 820 is passed with input planet
Input planetary gear 410 in dynamic component 400 rotates connection, and the periphery of the first periphery wheel portion 820 is additionally provided with driving cog.First
Center wheel portion 810 is in the center of the first planetary gear set 500, and the periphery of the first center wheel portion 810 also is provided with can be with first
The driving cog of the engaged transmission of class planetary gear 510.
Main gear ring 900 is located in gear box casing 100, and it can also opposed gear tank shell in the axial direction under external force
100 movements.In the present embodiment, the periphery of main gear ring 900 is provided with external splines 910, when the external splines 910 and gear box casing
Internal spline 110 in 100 can fix the circumferential position of the main opposed gear tank shell 100 of gear ring 900 when coordinating.Main gear ring 900
Inner circumferential is provided with the first ring gear portion 920 and the second ring gear portion 930, and the internal diameter in the first ring gear portion 920 is less than the second ring gear portion 930
External diameter, specifically, the first ring gear portion 920 can be engaged with first kind planetary gear 510, and the second ring gear portion 930 can be with second
The periphery wheel portion 820 of class planetary gear 610 and first is engaged.In the present invention, main gear ring 900 is in the axial direction under external force
When opposed gear tank shell 100 is moved, including the output shaft 300 of three transmission mechanisms that can realize the present invention has different turn
Three axial locations of speed：First axial location（Position shown in Fig. 2）, the second axial location（Position shown in Fig. 3）And the 3rd
Axial location（Position shown in Fig. 4）.
Simultaneously in order to realize that main gear ring 900 is cut in the first axial location, the second axial location, the 3rd axial location part
Change, transmission mechanism also includes a changer lever 940.
Introduce in detail below when main gear ring 900 is located at different axial locations, the transmission principle of transmission mechanism：
With reference to Fig. 1 and 2, under being acted in the switching of changer lever 940, when main gear ring 900 is located at the first axial location：Main tooth
The circumferential position for enclosing 900 opposed gear tank shells 100 is fixed, and it is by the external splines 910 and gearhousing on main gear ring 900
Internal spline 110 inside body 100 coordinates and fixes the circumferential position of winner's gear ring 900；And now first inside main gear ring 900
Ring gear portion 920 is engaged with first kind planetary gear 510, outside the second ring gear portion 930 and Equations of The Second Kind planetary gear 610 and first
All wheel portions 820 depart from.So, power is inputted by input centre wheel 420 first, and is slowed down by input planetary gear 410
After pass to central driving medium 800, and the first center wheel portion 810 in central driving medium 800 outputs power to Equations of The Second Kind
Planetary gear 610, now, because the opposed gear tank shell 100 of main gear ring 900 is fixed, now, Equations of The Second Kind planetary gear
610th, primary planet wheel carrier 700, first kind planetary gear 510 constitute a planetary gear train, after planetary gear train deceleration, power warp
The second center wheel portion 730 on primary planet wheel carrier 700 is exported to output end Gear Planet Transmission component 200, and is passed through output end planet
The final output of component 200 is moved to output shaft 300.So as in the first axial location, the first center wheel portion 810, Equations of The Second Kind planet tooth
Wheel 610, the ring gear portion 920 of first kind planetary gear 510 and first constitute a planetary gear train, its in the lump with input Gear Planet Transmission
Component 400, output end Gear Planet Transmission component 200 are driven so that output shaft 300 now has the first transmission speed.
Reference picture 1 and Fig. 3, under being acted in the switching of changer lever 940, when main gear ring 900 is located at the second axial location：It is main
The circumferential position of the opposed gear tank shell 100 of gear ring 900 is fixed, and it is by the external splines 910 and gear-box on main gear ring 900
Internal spline 110 inside housing 100 coordinates and fixes the circumferential position of winner's gear ring 900；And now inside main gear ring 900
One ring gear portion 920 departs from first kind planetary gear 510, and the second ring gear portion 930 is engaged with Equations of The Second Kind planetary gear 610.So,
Power is inputted by input centre wheel 420 first, and by passing to central driving medium after the deceleration of input planetary gear 410
800, and the first center wheel portion 810 in central driving medium 800 outputs power to Equations of The Second Kind planetary gear 610, now, because
Fixed for the main opposed gear tank shell 100 of gear ring 900, so now, Equations of The Second Kind planetary gear 610, primary planet wheel carrier 700,
Two ring gear portions 930 constitute a planetary gear train, and after planetary gear train deceleration, power is through in second on primary planet wheel carrier 700
Heart wheel portion 730 is exported to output end Gear Planet Transmission component 200, and through the final output of output end Gear Planet Transmission component 200 to output
Axle 300.So as to, in the second axial location, because now first kind planetary gear 510 is in idling conditions, so that, the first center
Wheel portion 810, Equations of The Second Kind planetary gear 610, the second ring gear portion 930 star wheel series in a row, its in the lump with input epicyclic gearsets
Part 400, output end Gear Planet Transmission component 200 are driven so that output shaft 300 now has the second transmission speed.
Reference picture 1 and Fig. 4, under being acted in the switching of changer lever 940, when main gear ring 900 is located at three axial locations：It is main
External splines 910 on gear ring 900 departs from the internal spline 110 inside gear box casing 100 to be coordinated, and main gear ring 900 can relative tooth
Take turns circumferentially rotating for tank shell 100；And now the first ring gear portion 920 inside main gear ring 900 takes off with first kind planetary gear 510
From the second ring gear portion 930 is engaged with the periphery wheel portion 820 of Equations of The Second Kind planetary gear 610 and first.So, power is first by defeated
Enter to hold centre wheel 420 to input, and pass to central driving medium 800 after slowing down by input planetary gear 410, and center driving
The first center wheel portion 810 on part 800 outputs power to Equations of The Second Kind planetary gear 610 again, now, because the phase of main gear ring 900
Gear box casing 100 is circumferentially rotated, the main synchronous axial system of 900 and first center wheel portion of gear ring 810 is that is to say, therefore, now
Two class planetary gears 610 are without rotation so that the center wheel portion 810 of primary planet wheel carrier 700 and first is with same rotating speed, i.e., and the
Two class planetary gears 610, without rotation, do not slow down, directly by power through primary planet wheel with first kind planetary gear 510
The second center wheel portion 730 on frame 700 is exported to output end Gear Planet Transmission component 200, and through output end Gear Planet Transmission component 200
Final output is to output shaft 300.So as in the 3rd axial location, because now first kind planetary gear 510 is in idle running shape
State, Equations of The Second Kind planetary gear 610 does not play decelerating effect with first kind planetary gear 510, only passes through input Gear Planet Transmission
Component 400, output end Gear Planet Transmission component 200 are driven so that output shaft 300 now has the 3rd transmission speed.
To sum up, transmission mechanism of the invention is by switching the axially different position of main gear ring 900 so that transmission mechanism has
Different transmission speed ratios, output shaft 300 has different output speeds,.
The present invention also proposes a kind of torque output instrument, and it includes the transmission mechanism of instrument casing, motor and the present invention,
Torque output instrument free switching under different operating rates is caused by the transmission mechanism of the present invention.
Show and stated above the basic principles, principal features and advantages of the present invention.The technical staff of the industry should
Solution, the invention is not limited in any way for above-described embodiment, all skills obtained by the way of equivalent substitution or equivalent transformation
Art scheme, all falls within protection scope of the present invention.
Claims (10)
1. a kind of transmission mechanism, including：Gear box casing, the central driving medium that can be pivoted by axle of first axle, primary planet wheel
Frame, the main gear ring that can be axially moveable in the gearhousing body；Characterized in that, the transmission mechanism also includes：Respectively
The first planetary gear set and the second planetary gear set at the axially different position of primary planet wheel carrier, first planetary gear
Group includes more than two first kind planetary gears, and second planetary gear set includes more than two Equations of The Second Kind planetary gears,
The central driving medium includes：The first center engaged in the first planetary gear set center with the first kind planetary gear
The periphery of wheel portion, the first periphery wheel portion, first center wheel portion and first periphery wheel portion is equipped with driving cog；The master
Gear ring at least provided with：The the first ring gear portion that can be engaged with the first kind planetary gear, it can be nibbled with the Equations of The Second Kind planetary gear
The the second ring gear portion closed or can engaged with the Equations of The Second Kind planetary gear and first periphery wheel portion, the main gear ring is in axle
At least have upwards：Make the first axial location that the first ring gear portion engages with the first kind planetary gear, make described
The second axial location that two ring gear portions are only engaged with the Equations of The Second Kind planetary gear, make the second ring gear portion and the Equations of The Second Kind
The 3rd position that planetary gear and first periphery wheel portion are engaged.
2. transmission mechanism according to claim 1, it is characterised in that the first planetary gear set described in the axial direction is located at described
The front side of second planetary gear set.
3. transmission mechanism according to claim 2, it is characterised in that the front end of the primary planet wheel carrier is also formed with one
Second center wheel portion, the periphery of second center wheel portion is provided with driving cog.
4. transmission mechanism according to claim 3, it is characterised in that the transmission mechanism also includes：One output shaft and
One output end Gear Planet Transmission component, the output end Gear Planet Transmission component includes：Two or more and second center wheel portion
The output end planetary gear of engagement, output end planetary wheel carrier, an output end gear ring；The output end planetary wheel carrier and institute
State output shaft and constitute transmission.
5. transmission mechanism according to claim 1, it is characterised in that the first kind planetary gear and the Equations of The Second Kind row
The relatively described first axle of star gear is symmetrical arranged.
6. transmission mechanism according to claim 5, it is characterised in that the first kind planetary gear and the Equations of The Second Kind row
The number of star gear is identical and setting is corresponded in the circumference of the primary planet wheel carrier.
7. transmission mechanism according to claim 6, it is characterised in that positioned at the same circumferential position of primary planet wheel carrier
The planetary wheel overlapping of axles of first kind planetary gear and the Equations of The Second Kind.
8. transmission mechanism according to claim 7, it is characterised in that the planetary tooth radius of the first kind is less than
The planetary tooth radius of Equations of The Second Kind.
9. transmission mechanism according to claim 1, it is characterised in that the transmission mechanism also includes：It is more than two defeated
Enter to hold planetary gear, input centre wheel, an input gear ring；The central driving medium rotates the connection input
Planetary gear, the input planetary gear is engaged with the input centre wheel.
10. a kind of torque output instrument, including：Instrument casing, motor, it is characterised in that also include：Such as claim 1 to 9 times
Transmission mechanism described in meaning one.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410308024.3A CN105333072B (en) | 2014-06-30 | 2014-06-30 | torque output tool and transmission mechanism thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410308024.3A CN105333072B (en) | 2014-06-30 | 2014-06-30 | torque output tool and transmission mechanism thereof |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105333072A CN105333072A (en) | 2016-02-17 |
| CN105333072B true CN105333072B (en) | 2017-08-29 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410308024.3A Expired - Fee Related CN105333072B (en) | 2014-06-30 | 2014-06-30 | torque output tool and transmission mechanism thereof |
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| Country | Link |
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Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105697692A (en) * | 2016-04-08 | 2016-06-22 | 群胜科技（苏州）有限公司 | Electric tool gear case speed change structure |
| CN115889855A (en) * | 2021-09-30 | 2023-04-04 | 南京泉峰科技有限公司 | Electric drill |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1583370A (en) * | 2003-05-30 | 2005-02-23 | 创科实业有限公司 | Three speed rotary power tool |
| CN2828444Y (en) * | 2005-07-12 | 2006-10-18 | 苏州宝时得电动工具有限公司 | Three-speed gear box |
| CN101220859A (en) * | 2006-02-03 | 2008-07-16 | 布莱克和戴克公司 | Electrical tools |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4053865B2 (en) * | 2002-11-12 | 2008-02-27 | 株式会社マキタ | Electric tool |
| DE202004014986U1 (en) * | 2004-09-25 | 2006-02-02 | A & M Electric Tools Gmbh | Planetary gear |
-
2014
- 2014-06-30 CN CN201410308024.3A patent/CN105333072B/en not_active Expired - Fee Related
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1583370A (en) * | 2003-05-30 | 2005-02-23 | 创科实业有限公司 | Three speed rotary power tool |
| CN2828444Y (en) * | 2005-07-12 | 2006-10-18 | 苏州宝时得电动工具有限公司 | Three-speed gear box |
| CN101220859A (en) * | 2006-02-03 | 2008-07-16 | 布莱克和戴克公司 | Electrical tools |
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| CN105333072A (en) | 2016-02-17 |
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Address after: 211106 No. 529, 159, Jiangjun Avenue, Jiangning District, Nanjing, Jiangsu Province Patentee after: Nanjing Quanfeng Technology Co.,Ltd. Address before: 211106, No. 159, general road, Jiangning economic and Technological Development Zone, Nanjing, Jiangsu Patentee before: NANJING CHERVON INDUSTRY Co.,Ltd. |
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Granted publication date: 20170829 |