CN201610930U - Power split type combined planetary speed reducer - Google Patents
Power split type combined planetary speed reducer Download PDFInfo
- Publication number
- CN201610930U CN201610930U CN2009202832647U CN200920283264U CN201610930U CN 201610930 U CN201610930 U CN 201610930U CN 2009202832647 U CN2009202832647 U CN 2009202832647U CN 200920283264 U CN200920283264 U CN 200920283264U CN 201610930 U CN201610930 U CN 201610930U
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- Prior art keywords
- gear
- differential
- planetary
- gear pair
- type combined
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/04—Combinations of toothed gearings only
- F16H37/041—Combinations of toothed gearings only for conveying rotary motion with constant gear ratio
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/2809—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels
- F16H1/2836—Toothed gearings for conveying rotary motion with gears having orbital motion with means for equalising the distribution of load on the planet-wheels by allowing limited movement of the planets relative to the planet carrier or by using free floating planets
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
Abstract
The utility model discloses a power split type combined planetary speed reducer which comprises an input gear pair, a differential planetary gear pair, a closed planetary gear pair arranged between the input gear pair and the differential planetary gear pair, a flexible shaft and a support rod, wherein only the support rod is arranged on the ground through a torsion frame mechanism, and the torsion frame mechanism can absorb vibration, angular deviation and displacement generated during the operation of a grinder, and not affect gears and a bearing, thus prolonging the service life of parts; and a planetary rotating frame of the differential planetary gear pair is an output flange which carries out a small part of torque transfer, a closed internal gear ring of the closed planetary gear pair is connected with the output flange so as to transfer a large part of torque, that is the output flange and the closed internal gear ring are adopted for common shunt and output of the torque, thereby being safe and reliable, having compact structure, small volume and light weight, and greatly saving the manufacturing cost; and the adoption of the direction connection way of the output flange can eliminate a transmission shaft, have light weight and compact structure, greatly reduce the layout size and reduce the construction investment in plants.
Description
Technical field
The utility model relates to a kind of speed reducer, the power shunt type combined planetary reducer of especially a kind of high-power, large speed ratio and small volume.
Background technique
The center gearing speed-reducer is generally power bi-shunting, double reduction, symmetric arrangement, coaxial structure at present.Main motor links by the first order pinion shaft of shaft coupling and main reducing gear, and one-level small gear and two gearwheel engagements are finished chopped-off head and slowed down; The one-level gearwheel is connected with the secondary small gear by flexible shaft, and the secondary small gear meshes with gearwheel again, carries out double reduction, and moment of torsion is passed to grinding machine.Deficiency is that technology arrangement is taken up an area of greatly, cost is high, the cycle is long.
The model utility content
The utility model is at the deficiencies in the prior art, a kind of power shunt type combined planetary reducer is provided, it generally adopts power bi-shunting, double reduction driving mechanism at present center gearing speed-reducer, transmission speed is smaller, volume is also bigger, and need the practical problem of a large amount of grounds, a kind of new power shunt type combined planetary reducer is provided.
For realizing above technical purpose, the utility model will be taked following technological scheme:
A kind of power shunt type combined planetary reducer, comprise the input gear pair, the differential planet gear pair, place the closed planetary gear pair between input gear pair and the differential planet gear pair, flexible shaft and strut, flexible shaft is supported on the strut by clutch shaft bearing, strut is supported in foundation of civil work by ball bearing, and flexible shaft is a load balancing mechanism, described input gear pair, comprise input shaft, driving gear and driven gear, input shaft passes through second bearings on strut, driving gear and input shaft are connected, driven gear then is connected with flexible shaft, and driving gear is meshed with driven gear; Described closed planetary gear pair, comprise sealing sun gear, sealing ring gear, closed planetary wheel, closed planetary axle and static planet carrier, the sealing sun gear floats and is placed on the flexible shaft, the closed planetary wheel is supported on the static planet carrier by the closed planetary axle, and this static planet carrier is connected with strut; Described differential planet gear pair, comprise differential sun gear, differential ring gear, differential planetary gear train, differential planetary elastic axis and output flange, flexible shaft one end is differential sun gear, differential planetary gear train is installed on the output flange by the differential planetary elastic axis, and described differential planetary elastic axis is a load balancing mechanism; In addition, differential ring gear is connected with the sealing sun gear by flexible carrier, and the sealing ring gear then is connected with output flange.
The differential planetary elastic axis comprises bearing pin and the 3rd bearing, described bearing pin cantilever is provided with, this bearing pin cantilever end and output flange are connected, the opposite end of bearing pin cantilever end then is connected with baffle plate, Spielpassung is connected with resilient sleeve on the described bearing pin axis body, and this resilient sleeve one end nestles up the baffle plate setting, and the barrel outer surface of the other end is provided with the sleeve seam, the 3rd Bearing Installation is between sleeve seam and baffle plate, and differential planetary gear train is connected with the differential planetary elastic axis by the 3rd bearing.
Also press between described the 3rd bearing and the baffle plate and be provided with distance ring, this distance ring is coated on the resilient sleeve periphery.
Offer groove on the bearing pin axis body that described resilient sleeve coated.
Be provided with between described static planet carrier and the sealing sun gear and be used for differential ring gear and the wear-resistant vibration-damping thrust device that seals sun gear connecting body axial limiting, this wear-resistant vibration-damping thrust device comprises steel base, elastomeric plastics thrust layer and damping spring layer, described elastomeric plastics thrust layer is arranged between steel base and the sealing sun gear, and the damping spring layer then is arranged between steel base and the static planet carrier.
Described elastomeric plastics thrust layer adopts polytetrafluoroethylmaterial material to be made, and this elastomeric plastics thrust layer directly to bind by binding agent with steel base be one.
Described elastomeric plastics thrust layer adopts the modified Teflon material to form, and this elastomeric plastics thrust layer and steel base are welded as a whole by brazing mode.
Described driving gear and driven gear all adopt the involute profile hardened face gear.
Flexible shaft is a hollow shaft.
Comprise respectively more than three in described differential planet gear pair and the closed planetary gear pair and be distributed in corresponding sun gear planet wheel on every side according to annular array.
According to above technological scheme, can realize following beneficial effect:
Speed reducer described in the utility model, its output flange rotates with grinding mill barrel, has only torque stand mechanism to land, the vibration that torque stand mechanism produces in the time of can absorbing mill running, angular variation and displacement, gear and bearing are not exerted an influence, in the elongated component life-span, guarantee reliable operation; Adopt differential stage planet carrier (being output flange) and enclosure class ring gear to shunt output torque jointly, safer, reliable, compact structure, volume is little, and is in light weight, saved a large amount of speed reducer manufacture costs; Adopt the output flange straight connection type, saved transmission shaft, in light weight, compact structure has shortened the layout size greatly, reduces the workshop building investment; Speed reducer described in the utility model need not to design the foundation of civil work that bears the big load of speed reducer, and the construction investment expense of having saved has shortened the whole manufacturing cycle simultaneously.
Description of drawings
Fig. 1 is a kind of structural representation of the present utility model;
Fig. 2 is an another kind of structural representation of the present utility model;
Fig. 3 is the structure for amplifying schematic representation of differential planetary elastic axis described in the utility model;
Fig. 4 is the structure for amplifying schematic representation of the pairing wear-resistant vibration-damping thrust device of II part among Fig. 2;
Fig. 5 a is the structural representation of wear-resistant vibration-damping thrust device; Fig. 5 b is the A-A sectional view of Fig. 5 a.
Among the figure, input shaft 11 driving gears 12 driven gears 13 flexible shafts 2 sealing sun gears 31 closed planetary axles 32 closed planetaries wheel 33 sealing ring gears 34 static planet carrier 35 struts 41 joint shaft bearings 42 differential planetary gear trains 51 differential planetary elastic axiss 52 output flanges 53 differential ring gear 54 the 3rd bearing 55 resilient sleeves 56 baffle plates 57 distance rings 58 flexible carriers 6 elastomeric plastics thrust layers 71 steel base 72 damping spring layers 73.
Embodiment
Explain the technical solution of the utility model below with reference to accompanying drawing.
Embodiment 1
As shown in Figure 1, power shunt type combined planetary reducer described in the utility model, comprise the input gear pair, the differential planet gear pair, place the closed planetary gear pair between input gear pair and the differential planet gear pair, flexible shaft 2 and strut 41, flexible shaft 2 is supported on the strut 41 by clutch shaft bearing, these strut 41 two ends are supported in the torque stand mechanism by joint shaft bearing, and torque stand mechanism is fixed on the foundation of civil work, and flexible shaft 2 is load balancing mechanisms, described input gear pair, comprise input shaft 11, driving gear 12 and driven gear 13, input shaft 11 passes through second bearings on strut 41, driving gear 12 is connected with input shaft 11, driven gear 13 then is connected with flexible shaft 2, and driving gear 12 is meshed with driven gear 13; Described closed planetary gear pair, comprise sealing sun gear 31, sealing ring gear 34, closed planetary wheel 33, closed planetary axle 32 and static planet carrier 35, sealing sun gear 31 floats and is placed on the flexible shaft 2, closed planetary wheel 33 is supported on the static planet carrier 35 by closed planetary axle 32, and this static planet carrier 35 is connected with strut 41; Described differential planet gear pair, comprise differential sun gear, differential ring gear 54, differential planetary gear train 51, differential planetary elastic axis 52 and output flange 53, flexible shaft 2 one ends are differential sun gear, differential planetary gear train 51 is installed on the output flange 53 by differential planetary elastic axis 52, to transmit the moment of fraction, described differential planetary elastic axis 52 is load balancing mechanisms; In addition, differential ring gear 54 is connected with sealing sun gear 31 by flexible carrier 6, and sealing ring gear 34 then is connected with output flange 53, and to transmit most moment, therefore, described differential ring gear 54 and sealing sun gear 31 are to float to be provided with.
Differential planetary elastic axis 52 is a cantilever structure, as shown in Figure 3, this differential planetary elastic axis 52 comprises bearing pin, described bearing pin cantilever is provided with, this bearing pin cantilever end and output flange 53 are connected, the opposite end of bearing pin cantilever end then is connected with baffle plate 57, Spielpassung is connected with resilient sleeve 56 on the described bearing pin axis body, these resilient sleeve 56 1 ends nestle up baffle plate 57 and are provided with, the barrel outer surface of the other end is provided with the sleeve seam, and the 3rd bearing 55 is installed between sleeve seam and the baffle plate 57, differential planetary gear train 51 is connected with differential planetary elastic axis 52 by the 3rd bearing 55, also press between described the 3rd bearing 55 and the baffle plate 57 and be provided with distance ring 58, this distance ring 58 is coated on resilient sleeve 56 peripheries, and offer groove on the bearing pin axis body that resilient sleeve 56 is coated, described the 3rd bearing 55 can be selfaligning roller bearing or tapered roller bearing, therefore, because differential planetary gear train 51 is subjected to two tangential forces: the angle amount of deflection that one of them causes from the bending of output flange 53 upper pins, the angle amount of deflection that another bending that then comes from resilient sleeve 56 causes, when these two tangential forces put on the differential planetary gear train 51 of differential planet gear pair simultaneously, because both directions are opposite, can cancel out each other, then the amount of deflection of each gear contacting point will followed a circular movement, this means the axis of gear contact will be not can be owing to the inaccuracy of angular positioning to laterally inclined, also can be leading owing to the torsional deflection of output flange 53; In addition, because gear has the tendency of less off-axis, the output flange 53 of single side no longer twists, can think that gear all has the probability of very high maintenance centering in all contact pointss, so when adopting this differential planetary elastic axis 52, even use the narrower gear of the facewidth, also still can avoid stress to concentrate, therefore the specific power at axial direction can improve.
In addition, described driving gear 12 and driven gear 13 all adopt the involute profile hardened face gear, described flexible shaft 2 is a hollow shaft, is distributed in corresponding sun gear planet wheel on every side and comprise respectively more than three in differential planet gear pair and the closed planetary gear pair according to annular array.
Embodiment's 2 described technological schemes are substantially the same manner as Example 1, just among the embodiment 2, between static planet carrier 35 and sealing sun gear 31, be provided with and be used for differential ring gear 54 and the wear-resistant vibration-damping thrust device that seals sun gear 31 connecting body axial limitings, this wear-resistant vibration-damping thrust device comprises steel base 72, elastomeric plastics thrust layer 71 and damping spring layer 73, described elastomeric plastics thrust layer 71 is arranged between steel base 72 and the sealing sun gear 31, and damping spring layer 73 then is arranged between steel base 72 and the static planet carrier 35.
Described elastomeric plastics thrust layer 71 adopts polytetrafluoroethylmaterial materials to be made, and this elastomeric plastics thrust layer 71 directly to bind by binding agent with steel base 72 be one; Perhaps this elastomeric plastics thrust layer 71 adopts modified Teflon material to form, and this elastomeric plastics thrust layer 71 and steel base 72 are welded as a whole by brazing mode.
In addition, described steel base 72 is provided with ringwise, and elastomeric plastics thrust layer 71 is distributed to be provided with according to annular array by a plurality of resilient pads and forms, simultaneously, resilient pad of every installation on steel base 72, at the opposing side of steel base 72 a slice butterfly spring is installed accordingly, promptly damping spring layer 73 is to be formed according to the form setting that annular array distributes by the multi-disc butterfly spring, and resilient pad, steel base 72 and butterfly spring link into an integrated entity by threaded fastener.
Because the friction layer of wear-resistant vibration-damping thrust device described in the utility model is an elastomeric plastics thrust layer 71, material adopts the teflon of teflon or modification, has the little (dry friction: 0.16～0.22 of friction factor; Drop lubrication: 0.013～0.040), chemical stability is good, advantages such as thermal conductivity is little, especially with friction pair to when mill, its surface layer teflon shifts to surface of friction pair, forms more stable teflon solid lubricant film, thereby under the oil-free lubrication condition, can have longer working life, and have under the condition of oil lubrication, increase exponentially its working life especially.Damping spring layer 73 is made up of one or one group of damping spring; the damping spring of Shi Yonging has that the buffering vibration absorption ability is strong, the axial space position takies little characteristics herein; can effectively alleviate because the impact that the speed reducer vibration causes; protection elastomeric plastics thrust layer 71 is not damaged by rigid impulse, thereby guarantees the safe and reliable work of this wear-resistant vibration-damping thrust device.
Therefore; when speed reducer vibration causing differential stage ring gear and sealing sun gear 31 connecting body generation axial floats; and when contacting with wear-resistant vibration-damping thrust device; elastomeric plastics thrust layer 71 is contact friction face; its material has the excellent abrasive energy; can effectively protect revolving meber and wear-resistant vibration-damping thrust device itself not to be subjected to frictionally damage, and damping spring layer 73 can absorb impact force, can effectively protect revolving meber and wear-resistant vibration-damping thrust device not damaged by rigid impulse.
Claims (10)
1. power shunt type combined planetary reducer, it is characterized in that: comprise input gear pair, differential planet gear pair, place closed planetary gear pair, flexible shaft and strut between input gear pair and the differential planet gear pair, flexible shaft is supported on the strut by clutch shaft bearing, strut is supported in foundation of civil work by ball bearing, wherein:
The input gear pair comprises input shaft, driving gear and driven gear, and on strut, driving gear and input shaft are connected input shaft by second bearings, and driven gear then is connected with flexible shaft, and driving gear is meshed with driven gear;
The closed planetary gear pair, comprise sealing sun gear, sealing ring gear, closed planetary wheel, closed planetary axle and static planet carrier, the sealing sun gear floats and is placed on the flexible shaft, and the closed planetary wheel is supported on the static planet carrier by the closed planetary axle, and this static planet carrier is connected with strut;
The differential planet gear pair, comprise differential sun gear, differential ring gear, differential planetary gear train, differential planetary elastic axis and output flange, flexible shaft one end is differential sun gear, differential planetary gear train is installed on the output flange by the differential planetary elastic axis, and described differential planetary elastic axis is a load balancing mechanism;
Differential ring gear is connected with the sealing sun gear by flexible carrier, and the sealing ring gear then is connected with output flange.
2. power shunt type combined planetary reducer according to claim 1, it is characterized in that, the differential planetary elastic axis comprises bearing pin and the 3rd bearing, described bearing pin cantilever is provided with, this bearing pin cantilever end and output flange are connected, the opposite end of bearing pin cantilever end then is connected with baffle plate, Spielpassung is connected with resilient sleeve on the described bearing pin axis body, this resilient sleeve one end nestles up the baffle plate setting, the barrel outer surface of the other end is provided with the sleeve seam, the 3rd Bearing Installation is between sleeve seam and baffle plate, and differential planetary gear train is connected with the differential planetary elastic axis by the 3rd bearing.
3. power shunt type combined planetary reducer according to claim 2 is characterized in that, also presses between described the 3rd bearing and the baffle plate to be provided with distance ring, and this distance ring is coated on the resilient sleeve periphery.
4. power shunt type combined planetary reducer according to claim 2 is characterized in that, offers groove on the bearing pin axis body that described resilient sleeve coated.
5. power shunt type combined planetary reducer according to claim 1, it is characterized in that, be provided with between described static planet carrier and the sealing sun gear and be used for differential ring gear and the wear-resistant vibration-damping thrust device that seals sun gear connecting body axial limiting, this wear-resistant vibration-damping thrust device comprises steel base, elastomeric plastics thrust layer and damping spring layer, described elastomeric plastics thrust layer is arranged between steel base and the sealing sun gear, and the damping spring layer then is arranged between steel base and the static planet carrier.
6. power shunt type combined planetary reducer according to claim 5 is characterized in that, described elastomeric plastics thrust layer adopts polytetrafluoroethylmaterial material to be made, and this elastomeric plastics thrust layer directly to bind by binding agent with steel base be one.
7. power shunt type combined planetary reducer according to claim 5 is characterized in that, described elastomeric plastics thrust layer adopts the modified Teflon material to form, and this elastomeric plastics thrust layer and steel base are welded as a whole by brazing mode.
8. power shunt type combined planetary reducer according to claim 1 is characterized in that described driving gear and driven gear all adopt the involute profile hardened face gear.
9. power shunt type combined planetary reducer according to claim 1 is characterized in that, flexible shaft is a hollow shaft.
10. according to the described power shunt type combined planetary reducer of 1 to 9 arbitrary claim, it is characterized in that, comprise respectively more than three in the secondary and closed planetary gear pair of described differential planet gear and be distributed in corresponding sun gear planet wheel on every side according to annular array.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009202832647U CN201610930U (en) | 2009-12-30 | 2009-12-30 | Power split type combined planetary speed reducer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009202832647U CN201610930U (en) | 2009-12-30 | 2009-12-30 | Power split type combined planetary speed reducer |
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| Publication Number | Publication Date |
|---|---|
| CN201610930U true CN201610930U (en) | 2010-10-20 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009202832647U Expired - Lifetime CN201610930U (en) | 2009-12-30 | 2009-12-30 | Power split type combined planetary speed reducer |
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| CN (1) | CN201610930U (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101737476B (en) * | 2009-12-30 | 2012-02-29 | 南京高精齿轮集团有限公司 | Power shunt type combined planetary reducer |
| CN103291845A (en) * | 2013-06-17 | 2013-09-11 | 西北工业大学 | Automatic uniform loading device of power dividing gear system |
| CN103968003A (en) * | 2014-05-20 | 2014-08-06 | 西北工业大学 | Torque shunting transmission mechanism for helicopter main reducing gear |
| CN105082977A (en) * | 2014-05-22 | 2015-11-25 | 福特全球技术公司 | Clutch control to enter powersplit hybrid powertrain parallel mode |
| CN105151042A (en) * | 2014-05-22 | 2015-12-16 | 福特全球技术公司 | Entering and exiting parallel operation of a powersplit hybrid powertrain |
| CN107415320A (en) * | 2017-06-08 | 2017-12-01 | 深圳市科发机械制造有限公司 | It is die cut roller apparatus and printing and die-cutting apparatus |
-
2009
- 2009-12-30 CN CN2009202832647U patent/CN201610930U/en not_active Expired - Lifetime
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101737476B (en) * | 2009-12-30 | 2012-02-29 | 南京高精齿轮集团有限公司 | Power shunt type combined planetary reducer |
| CN103291845A (en) * | 2013-06-17 | 2013-09-11 | 西北工业大学 | Automatic uniform loading device of power dividing gear system |
| CN103291845B (en) * | 2013-06-17 | 2016-01-06 | 西北工业大学 | A kind of automatic load sharing device of power dividing gear system |
| CN103968003A (en) * | 2014-05-20 | 2014-08-06 | 西北工业大学 | Torque shunting transmission mechanism for helicopter main reducing gear |
| CN105082977A (en) * | 2014-05-22 | 2015-11-25 | 福特全球技术公司 | Clutch control to enter powersplit hybrid powertrain parallel mode |
| CN105151042A (en) * | 2014-05-22 | 2015-12-16 | 福特全球技术公司 | Entering and exiting parallel operation of a powersplit hybrid powertrain |
| CN105151042B (en) * | 2014-05-22 | 2019-01-04 | 福特全球技术公司 | Into and exit power dividing hybrid power power drive system parallel running method |
| CN107415320A (en) * | 2017-06-08 | 2017-12-01 | 深圳市科发机械制造有限公司 | It is die cut roller apparatus and printing and die-cutting apparatus |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| EE01 | Entry into force of recordation of patent licensing contract |
Assignee: Nanjing Gaojing Engineering Equipment Co., Ltd. Assignor: Nanjing High-Speed & Accurate Gear Manufacturing Co., Ltd. Contract record no.: 2011320000534 Denomination of utility model: Power shunt type combined planetary reducer Granted publication date: 20101020 License type: Exclusive License Record date: 20110407 |
|
| ASS | Succession or assignment of patent right |
Owner name: NANJING HIGH SPEED AND ACCURATE GEAR CO., LTD. Free format text: FORMER OWNER: NANJING HIGH ACCURATE HEAVY-DUTY GEAR MANUFACTURING CO., LTD. Effective date: 20110520 |
|
| C41 | Transfer of patent application or patent right or utility model | ||
| COR | Change of bibliographic data |
Free format text: CORRECT: ADDRESS; FROM: 210012 XIAOHANG, OUTER ZHONGHUAMEN, NANJING CITY, JIANGSU PROVINCE TO: 210012 NO. 3, YOUJIA AO, XIAOHANG, OUTER ZHONGHUAMEN, NANJING CITY, JIANGSU PROVINCE, CHINA |
|
| TR01 | Transfer of patent right |
Effective date of registration: 20110520 Address after: Outside the Chinese small home especially in Jiangsu province Nanjing city 210012 concave China No. 3 Patentee after: Nanjing High-Speed & Accurate Gear Group Co., Ltd. Address before: 210012 Jiangsu city of Nanjing province outside the Chinese small Patentee before: Nanjing High-Speed & Accurate Gear Manufacturing Co., Ltd. |
|
| AV01 | Patent right actively abandoned |
Granted publication date: 20101020 Effective date of abandoning: 20091230 |