CN105333072A - Torque output tool and transmission mechanism thereof - Google Patents
Torque output tool and transmission mechanism thereof Download PDFInfo
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- CN105333072A CN105333072A CN201410308024.3A CN201410308024A CN105333072A CN 105333072 A CN105333072 A CN 105333072A CN 201410308024 A CN201410308024 A CN 201410308024A CN 105333072 A CN105333072 A CN 105333072A
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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 moment of torsion and export instrument, be specifically related to a kind of moment of torsion and export instrument and driving mechanism thereof.
Background technique
Existing electric tool, because volume is little, lightweight, compact structure, transmission efficiency are high, velocity ratio is large, stable drive, shock resistance and anti-vibration ability strong, be therefore commercially in great demand especially.
At present, electric tool only has a kind of speed to export usually, and along with the requirement of people to electric tool performance more and more higher, wish that electric tool can have different transmission speed ratios according to actual needs.
Summary of the invention
For solving the deficiencies in the prior art, the object of the present invention is to provide a kind of driving mechanism with multiple different transmission speed ratio.
In order to realize above-mentioned target, the present invention adopts following technological scheme:
A kind of driving mechanism, comprising: gear box casing, can be with first axle the central driving medium of axle pivotable, primary planet wheel carrier, can the main gear ring of movement vertically in gear box casing; Driving mechanism also comprises: the first planet wheels and the second planetary gear set that are arranged on the axially different position of primary planet wheel carrier respectively, first planet wheels comprise plural first kind planetary pinion, second planetary gear set comprises plural Equations of The Second Kind planetary pinion, central driving medium comprises: the first central gear portion of engaging with first kind planetary pinion in first planet wheels center, the first wheel portion, periphery, and the periphery in the first central gear portion and the first wheel portion, periphery is equipped with driving cog; Main gear ring is at least provided with: the first ring gear portion can engaged with first kind planetary pinion, the second ring gear portion can engaged with Equations of The Second Kind planetary pinion or all can engage with Equations of The Second Kind planetary pinion and the first wheel portion, periphery, and main gear ring at least has in the axial direction: the first axial position that the first ring gear portion is engaged with first kind planetary pinion, the second axial position that the second ring gear portion is only engaged with Equations of The Second Kind planetary pinion, the 3rd position that the second ring gear portion is all engaged with Equations of The Second Kind planetary pinion and the first wheel portion, periphery.
Further, first planet wheels are positioned 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 central gear portion, and the periphery in the second central gear portion is provided with driving cog.
Further, driving mechanism also comprises: an output shaft and an output terminal Gear Planet Transmission assembly, and output terminal Gear Planet Transmission assembly comprises: the output terminal planetary pinion that two or more engages with the second central gear portion, output terminal planetary wheel carrier, an output terminal gear ring; Output terminal planetary wheel carrier and output shaft form transmission.
Further, first kind planetary pinion first axle all relative to Equations of The Second Kind planetary pinion is symmetrical arranged.
Further, first kind planetary pinion identical with the planetary number of Equations of The Second Kind and in the circumference of primary planet wheel carrier one_to_one corresponding arrange.
Further, the first kind planetary pinion and the planetary wheel shaft of Equations of The Second Kind that are positioned at the same circumferential position of primary planet wheel carrier overlap.
Further, the planetary tooth radius of the first kind is less than the planetary tooth radius of Equations of The Second Kind.
Further, driving mechanism also comprises: plural input end planetary pinion, input end central gear, an input end gear ring; Central driving medium is rotationally connected input end planetary pinion, and input end planetary pinion engages with input end central gear.
The present invention also proposes a kind of moment of torsion and exports instrument, comprising: instrument casing, motor, also comprise: above-described driving mechanism.
Usefulness of the present invention is: driving mechanism of the present invention is by switching the axially different position of main gear ring, driving mechanism is made to have different transmission speed ratios, output shaft has different output speeds, solve the problem that existing driving mechanism only has a kind of transmission output of speed, meet the demand of people to drive mechanism performance.
Accompanying drawing explanation
Figure 1 shows that the exploded perspective view of driving mechanism of the present invention;
Figure 2 shows that the partial cross section schematic diagram of the driving mechanism in Fig. 1, now main gear ring is positioned at the first axial position;
Figure 3 shows that the partial cross section schematic diagram of the driving mechanism in Fig. 1, now main gear ring is positioned at the second axial position;
Figure 4 shows that the partial cross section schematic diagram of the driving mechanism in Fig. 1, now main gear ring is positioned at the 3rd axial position.
Embodiment
Below in conjunction with the drawings and specific embodiments, concrete introduction is done to the present invention.
The present invention proposes a kind of driving mechanism, and this driving mechanism can be used in common moment of torsion output instrument, moment of torsion can be made to export instrument have different operating rates by this driving mechanism, and can under different operating rates freely.
Figure 1 shows that the exploded perspective view of driving mechanism of the present invention.Please refer to shown in Fig. 1, driving mechanism of the present invention (figure does not mark) comprising: gear box casing 100, output terminal Gear Planet Transmission assembly 200, output shaft 300, input end Gear Planet Transmission assembly 400, first planet wheels 500, second planetary gear set 600, primary planet wheel carrier 700, central driving medium 800, main gear ring 900, wherein output shaft 300 is as the final moment of torsion output of driving mechanism of the present invention, and it can around the first axle Y pivotable at self place.In the present invention, in order to clear, technological scheme of the present invention is described easily, make as given a definition especially, this definition is not as restriction essentiality content of the present invention: the direction at the first axle Y place of output shaft 300 and the direction being parallel to first axle Y are all defined as axis, direction around axis is circumference, outbound course towards output shaft 300 is front, after towards the direction contrary with outbound course of output shaft 300 being.
Figure 2 shows that the partial cross section schematic diagram of the driving mechanism in Fig. 1, now main gear ring is positioned at the first axial position.Please with reference to Fig. 1 and Fig. 2, gear box casing 100 is the shell of the driving mechanism in the present invention, for accommodating input end Gear Planet Transmission assembly 400, first planet wheels 500, second planetary gear set 600, primary planet wheel carrier 700, central driving medium 800, main gear ring 900.Concrete, in the present embodiment, the inner circumferential of gear box casing 100 is provided with the internal spline 110 that can coordinate with main gear ring 900.
Output terminal Gear Planet Transmission assembly 200 for by torque drive to output shaft 300, and by output shaft 300, moment of torsion is exported to workpiece to realize transmission agency.Output terminal Gear Planet Transmission assembly 200 comprises: output terminal planetary pinion 210, output terminal planetary wheel carrier 220 and output terminal gear ring 230.In the present embodiment, have multiple output terminal planetary pinion 210, the plurality of output terminal planetary pinion 210 is arranged at the rear side of output terminal planetary wheel carrier 220 and is rotationally connected with output terminal planetary wheel carrier 220.The rear side of output terminal planetary wheel carrier 220 is provided with and the equal corresponding planet pin 221 of output terminal planetary pinion 210 number and position, planet pin 221 for by sheathed for output terminal planetary pinion 210 its, thus output terminal planetary wheel carrier 220 and output terminal planetary pinion 210 are formed be in transmission connection; Output terminal planetary wheel carrier 220 is also in transmission connection with output shaft 300 by spline plectrum (figure does not mark), thus moment of torsion is exported to output shaft 300.Output terminal gear ring 230 is sheathed on outside multiple output terminal planetary pinion 210, and its inner circumferential is provided with driving cog, thus with output terminal planetary pinion 210 engagement fit, and output terminal ring gear opposed gear tank shell 100 circumferential position is fixed.
Input end Gear Planet Transmission assembly 400 comprises: input end planetary pinion 410, input end central gear 420 and input end gear ring 430.Input end central gear 420 is for introducing input end Gear Planet Transmission assembly 400 by the moment of torsion in the external world, and such as it can be connected with a motor-driven.Input end planetary pinion 410 comprises multiple, and multiple input end planetary pinions 410 are arranged at the periphery of input end central gear 420, and engages with its transmission.Input end gear ring 430 is sheathed on the outside of multiple input end planetary pinion 410, and form engagement driving with it, the periphery of input end gear ring 430 is also provided with peripheral structure 431, by this peripheral structure 431, input end gear ring 430 circumference is fixed on gear box casing 100.
First planet wheels 500, second planetary gear set 600 is arranged on the different axial position of primary planet wheel carrier 700 respectively, and first planet wheels 500 are also positioned at the front side of the second planetary gear set 600 in the axial direction.Concrete, first planet wheels 500 comprise multiple first kind planetary pinion 510, second planetary gear set 600 and comprise multiple Equations of The Second Kind planetary pinion 610, and primary planet wheel carrier 700 comprises wheel carrier body 710, driving pin 720 and the second central gear portion 730.Driving pin 720 on primary planet wheel carrier 700 is for installing first kind planetary pinion 510 and Equations of The Second Kind planetary pinion 610, and first kind planetary pinion 510 and Equations of The Second Kind planetary pinion 610 are fixedly mounted on primary planet wheel carrier 700 by the method for interference fit by driving pin 720, thus first kind planetary pinion 510, Equations of The Second Kind planetary pinion 610 and primary planet wheel carrier 700 is made to form synchronous axial system.Second central gear portion 730 is positioned at the front end of primary planet wheel carrier 700, it is in the lump along with primary planet wheel carrier 700 synchronous axial system, the periphery in the second central gear portion 730 is also provided with the driving cog engaged with the output terminal planetary pinion 210 in output terminal Gear Planet Transmission assembly 200, thus moment of torsion can be exported to output terminal Gear Planet Transmission assembly 200 by the second central gear portion 730 with engaging of output terminal planetary pinion 210 by primary planet wheel carrier 700.In the present embodiment, first planet wheels 500 comprise three first kind planetary pinions 510, three relative first axle Y of first kind planetary pinion 510 are symmetrical arranged, second planetary gear set 600 comprises three Equations of The Second Kind planetary pinions 610, three Equations of The Second Kind planetary pinions 610 also relatively first axle Y be also symmetrical arranged, the circumferential position of each Equations of The Second Kind planetary pinion 610 on primary planet wheel carrier 700 and the circumferential position one_to_one corresponding of first kind planetary pinion 510 on primary planet wheel carrier 700, and the wheel shaft of the corresponding first kind planetary pinion 510 of circumferential position and Equations of The Second Kind planetary pinion 610 overlaps, in the present embodiment, the radius being positioned at the first kind planetary pinion 510 of primary planet wheel carrier 700 front end is also less than the radius of the Equations of The Second Kind planetary pinion 610 being positioned at primary planet wheel carrier 700 rear end.
Central driving medium 800 is arranged at the front side of input end Gear Planet Transmission assembly 400, and it can around axial pivotable.Central driving medium 800 comprises: the first central gear portion 810 and the first wheel portion, periphery 820.First wheel portion, periphery 820 is rotationally connected with the input end planetary pinion 410 in input end Gear Planet Transmission assembly 400, and the first Lun Bu820 periphery, periphery is also provided with driving cog.First central gear portion 810 is in the center of first planet wheels 500, the periphery in the first central gear portion 810 be also provided with can with the driving cog of first kind planetary pinion 510 engagement driving.
Main gear ring 900 is positioned at gear box casing 100, and it can also move by opposed gear tank shell 100 in the axial direction under external force.In the present embodiment, the periphery of main gear ring 900 is provided with external splines 910, the circumferential position of main gear ring 900 opposed gear tank shell 100 can be fixed when this external splines 910 coordinates with the internal spline 110 in gear box casing 100.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 external diameter in the second ring gear portion 930, concrete, first ring gear portion 920 can engage with first kind planetary pinion 510, and the second ring gear portion 930 can engage with Equations of The Second Kind planetary pinion 610 and the first wheel portion, periphery 820.In the present invention, main gear ring 900 is when opposed gear tank shell 100 moves in the axial direction under external force, comprises three axial positions that three output shafts 300 that can realize driving mechanism of the present invention have different rotating speeds: the first axial position (shown in Fig. 2 position), the second axial position (shown in Fig. 3 position) and the 3rd axial position (shown in Fig. 4 position).
Simultaneously in order to realize the switching of main gear ring 900 at the first axial position, the second axial position, the 3rd axial position part, driving mechanism also comprises a changer lever 940.
Specifically introduce when main gear ring 900 is positioned at different axial positions below, the transmission principle of driving mechanism:
With reference to Fig. 1 and 2, when under the switching effect at changer lever 940, when main gear ring 900 is positioned at the first axial position: the circumferential position of main gear ring 900 opposed gear tank shell 100 is fixed, and it is coordinated with the internal spline 110 of gear box casing 100 inside by the external splines 910 on main gear ring 900 and winner's gear ring 900 circumferential position is fixed; And now the first ring gear portion 920 of main gear ring 900 inside engages with first kind planetary pinion 510, the second ring gear portion 930 departs from Equations of The Second Kind planetary pinion 610 and the first wheel portion, periphery 820.Like this, first power inputted by input end central gear 420, and pass to central driving medium 800 after being slowed down by input end planetary pinion 410, and the first central gear portion 810 in central driving medium 800 outputs power to Equations of The Second Kind planetary pinion 610, now, because main gear ring 900 opposed gear tank shell 100 is fixed, so now, Equations of The Second Kind planetary pinion 610, primary planet wheel carrier 700, first kind planetary pinion 510 forms a planetary gear train, after this planetary gear train slows down, the second central gear portion 730 of power on primary planet wheel carrier 700 exports output terminal Gear Planet Transmission assembly 200 to, and finally export output shaft 300 to through output terminal Gear Planet Transmission assembly 200.Thus, at the first axial position, first central gear portion 810, Equations of The Second Kind planetary pinion 610, first kind planetary pinion 510 and the first ring gear portion 920 form a planetary gear train, its in the lump with input end Gear Planet Transmission assembly 400, the transmission of output terminal Gear Planet Transmission assembly 200, make output shaft 300 now have the first transmission speed.
With reference to Fig. 1 and Fig. 3, when under the switching effect at changer lever 940, when main gear ring 900 is positioned at the second axial position: the circumferential position of main gear ring 900 opposed gear tank shell 100 is fixed, and it is coordinated with the internal spline 110 of gear box casing 100 inside by the external splines 910 on main gear ring 900 and winner's gear ring 900 circumferential position is fixed; And now the first ring gear portion 920 of main gear ring 900 inside departs from first kind planetary pinion 510, the second ring gear portion 930 engages with Equations of The Second Kind planetary pinion 610.Like this, first power inputted by input end central gear 420, and pass to central driving medium 800 after being slowed down by input end planetary pinion 410, and the first central gear portion 810 in central driving medium 800 outputs power to Equations of The Second Kind planetary pinion 610, now, because main gear ring 900 opposed gear tank shell 100 is fixed, so now, Equations of The Second Kind planetary pinion 610, primary planet wheel carrier 700, second ring gear portion 930 forms a planetary gear train, after this planetary gear train slows down, the second central gear portion 730 of power on primary planet wheel carrier 700 exports output terminal Gear Planet Transmission assembly 200 to, and finally export output shaft 300 to through output terminal Gear Planet Transmission assembly 200.Thus, at the second axial position, because now first kind planetary pinion 510 is in idling conditions, thus, first central gear portion 810, Equations of The Second Kind planetary pinion 610, second 930 one-tenth, ring gear portion one planetary gear train, its in the lump with input end Gear Planet Transmission assembly 400, the transmission of output terminal Gear Planet Transmission assembly 200, make output shaft 300 now have the second transmission speed.
With reference to Fig. 1 and Fig. 4, when under the switching effect at changer lever 940, when main gear ring 900 is positioned at the 3rd axial position: the external splines 910 on main gear ring 900 departs from the internal spline 110 of gear box casing 100 inside and coordinates, the circumference of main gear ring 900 energy opposed gear tank shell 100 is rotated; And now the first ring gear portion 920 of main gear ring 900 inside departs from first kind planetary pinion 510, the second ring gear portion 930 engages with Equations of The Second Kind planetary pinion 610 and the first wheel portion, periphery 820.Like this, first power inputted by input end central gear 420, and pass to central driving medium 800 after being slowed down by input end planetary pinion 410, and the first central gear portion 810 in central driving medium 800 outputs power to Equations of The Second Kind planetary pinion 610, now, because main gear ring 900 opposed gear tank shell 100 circumference is rotated, that is to say main gear ring 900 and the first central gear portion 810 synchronous axial system, therefore, now Equations of The Second Kind planetary pinion 610 does not have rotation, primary planet wheel carrier 700 is made to have same rotating speed with the first central gear portion 810, namely Equations of The Second Kind planetary pinion 610 and first kind planetary pinion 510 all do not have rotation, do not slow down, directly export the second central gear portion 730 of power on primary planet wheel carrier 700 to output terminal Gear Planet Transmission assembly 200, and finally export output shaft 300 to through output terminal Gear Planet Transmission assembly 200.Thus, at the 3rd axial position, because now first kind planetary pinion 510 is in idling conditions, Equations of The Second Kind planetary pinion 610 and first kind planetary pinion 510 do not play decelerating effect, by means of only input end Gear Planet Transmission assembly 400, the transmission of output terminal Gear Planet Transmission assembly 200, output shaft 300 is now made to have the 3rd transmission speed.
To sum up, driving mechanism of the present invention is by switching the axially different position of main gear ring 900, and make driving mechanism have different transmission speed ratios, output shaft 300 has different output speeds.
The present invention also proposes a kind of moment of torsion and exports instrument, and it comprises instrument casing, motor and driving mechanism of the present invention, makes moment of torsion export instrument freely switch under different operating rates by driving mechanism of the present invention.
More than show and stated basic principle of the present invention, major character and advantage.The technician of the industry should understand, and above-described embodiment does not limit the present invention in any form, the technological scheme that the mode that all employings are equal to replacement or equivalent transformation obtains, and all drops in protection scope of the present invention.
Claims (10)
1. a driving mechanism, comprising: gear box casing, can be with first axle the central driving medium of axle pivotable, primary planet wheel carrier, can the main gear ring of movement vertically in described gear box casing, it is characterized in that, described driving mechanism also comprises: the first planet wheels and the second planetary gear set that are arranged on the described axially different position of primary planet wheel carrier respectively, described first planet wheels comprise plural first kind planetary pinion, described second planetary gear set comprises plural Equations of The Second Kind planetary pinion, described central driving medium comprises: the first central gear portion of engaging with described first kind planetary pinion in described first planet wheels center, the first wheel portion, periphery, and the periphery in described first central gear portion and described first wheel portion, periphery is equipped with driving cog, described main gear ring is at least provided with: the first ring gear portion can engaged with described first kind planetary pinion, the the second ring gear portion can engaged with described Equations of The Second Kind planetary pinion or all can engage with described Equations of The Second Kind planetary pinion and described first wheel portion, periphery, described main gear ring at least has in the axial direction: make the first axial position that described first ring gear portion engages with described first kind planetary pinion, make the second axial position that described second ring gear portion only engages with described Equations of The Second Kind planetary pinion, make the 3rd position that described second ring gear portion all engages with described Equations of The Second Kind planetary pinion and described first wheel portion, periphery.
2. driving mechanism according to claim 1, is characterized in that, described in the axial direction first planet wheels are positioned at the front side of described second planetary gear set.
3. driving mechanism according to claim 2, is characterized in that, the front end of described primary planet wheel carrier is also formed with a second central gear portion, and the periphery in described second central gear portion is provided with driving cog.
4. driving mechanism according to claim 3, it is characterized in that, described driving mechanism also comprises: an output shaft and an output terminal Gear Planet Transmission assembly, and described output terminal Gear Planet Transmission assembly comprises: the output terminal planetary pinion that two or more engages with described second central gear portion, output terminal planetary wheel carrier, an output terminal gear ring; Described output terminal planetary wheel carrier and described output shaft form transmission.
5. driving mechanism according to claim 1, is characterized in that, described first kind planetary pinion described first axle all relative to described Equations of The Second Kind planetary pinion is symmetrical arranged.
6. driving mechanism according to claim 5, is characterized in that, described first kind planetary pinion identical with the planetary number of described Equations of The Second Kind and in the circumference of described primary planet wheel carrier one_to_one corresponding arrange.
7. driving mechanism according to claim 6, is characterized in that, the described first kind planetary pinion and the planetary wheel shaft of described Equations of The Second Kind that are positioned at the same circumferential position of described primary planet wheel carrier overlap.
8. driving mechanism according to claim 7, is characterized in that, the planetary tooth radius of the described first kind is less than the planetary tooth radius of described Equations of The Second Kind.
9. driving mechanism according to claim 1, is characterized in that, described driving mechanism also comprises: plural input end planetary pinion, input end central gear, an input end gear ring; Described central driving medium is rotationally connected described input end planetary pinion, and described input end planetary pinion engages with described input end central gear.
10. moment of torsion exports an instrument, comprising: instrument casing, motor, is characterized in that, also comprises: the driving mechanism as described in claim 1 to 9 any 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 |
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| Publication Number | Publication Date |
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| CN105333072A true CN105333072A (en) | 2016-02-17 |
| CN105333072B CN105333072B (en) | 2017-08-29 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201410308024.3A Active CN105333072B (en) | 2014-06-30 | 2014-06-30 | torque output tool and transmission mechanism thereof |
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Cited By (1)
| 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 |
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| JP2004160592A (en) * | 2002-11-12 | 2004-06-10 | Makita Corp | Power tool |
| CN1583370A (en) * | 2003-05-30 | 2005-02-23 | 创科实业有限公司 | Three speed rotary power tool |
| US20060068968A1 (en) * | 2004-09-25 | 2006-03-30 | A + M Electric Tools Gmbh | Planetary Gearbox |
| 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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2014
- 2014-06-30 CN CN201410308024.3A patent/CN105333072B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2004160592A (en) * | 2002-11-12 | 2004-06-10 | Makita Corp | Power tool |
| CN1583370A (en) * | 2003-05-30 | 2005-02-23 | 创科实业有限公司 | Three speed rotary power tool |
| US20060068968A1 (en) * | 2004-09-25 | 2006-03-30 | A + M Electric Tools Gmbh | Planetary Gearbox |
| 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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| Publication number | Priority date | Publication date | Assignee | Title |
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| 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 |
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| Publication number | Publication date |
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| CN105333072B (en) | 2017-08-29 |
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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. |