CN100523544C - Retarder - Google Patents
Retarder Download PDFInfo
- Publication number
- CN100523544C CN100523544C CNB2007100890198A CN200710089019A CN100523544C CN 100523544 C CN100523544 C CN 100523544C CN B2007100890198 A CNB2007100890198 A CN B2007100890198A CN 200710089019 A CN200710089019 A CN 200710089019A CN 100523544 C CN100523544 C CN 100523544C
- Authority
- CN
- China
- Prior art keywords
- gear
- mentioned
- input shaft
- connect
- swing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Landscapes
- Retarders (AREA)
Abstract
To provide an oscillating internally meshing planetary gear reducer capable of realizing a low cost and a high speed reduction ratio, the oscillating internally meshing type planetary gear reducer is constituted so as to include: an input shaft provided with an input gear which is circumscribed and meshed with a pinion provided on a motor; an input shaft gear formed on the input shaft; a plurality of eccentric body shafts each provided with an eccentric body for oscillating an oscillating external gear; an eccentric body shaft gear which is formed on each eccentric body shaft; and a distributing gear which is meshed with the input shaft gear and the eccentric body shaft gear.
Description
Technical field
Connect the engagement type plane table thermoconductivity meter of swing in the present invention relates to.
Background technique
In the past, known (Japan) spy open 2002-No. 106650 communiques or (Japan) spy open 2002-No. 122190 described gear motors 1,2 of communique and 2 '.
Fig. 6 represents that the spy opens the described gear motor 1 of communique 2002-No. 106650.Fig. 7 represents that the spy opens the described gear motor 2 of communique 2002-No. 122190.Fig. 8 represent the spy open 2002-No. 122190 described gear motors 2 of communique '.Also have,, attachedly describe with same-sign about the identical or similar part of these each gear motors.
Each gear motor includes motor 10 as power source, be equipped in small gear or belt wheel 14 on the motor shaft 12 of motor 10, possess the carrier 38 (38A, 38B) of the rotation composition of the eccentric axon 30 of the eccentric body 32 that is used to swing external tooth gear 34 and unloading external tooth gear 34, and this carrier 38 spool is bearing on the housing 40 with bearing 50 (50A, 50B) by carrier.
In gear motor 1, distribution gear 26 engagements in small gear 14 and big footpath, each input gear 20 that (only showing 1 among Fig. 3) possesses on the small gear 26A that forms on this distribution gear 26 and the 3 eccentric axons 30 meshes.In addition, this distribution gear 26 is by bearing 80,81 rotations supporting freely.
In gear motor 2, small gear 14 directly with eccentric axon 30 (in 3 eccentric shafts 30 1, only show 1 among Fig. 4) on input gear 20 engagements that possess.Also have this input gear 20 and distribution gear 26 engagements, the input gear 20 (all not having diagram) that possesses respectively on this distribution gear 26 and other two eccentric axons 30 engagement.That is, dispose 3 eccentric axons 30 (30A, 30B, 30C) that possess input gear 20 (20A, 20B, 20C), wherein import gear 20A and small gear 14 and distribution gear 26 engagements for 1, other input gears 20B, 20C only mesh with distribution gear 26.In addition, distribution gear 26 is by bearing 80,81 rotations supporting freely.
Gear motor 2 ' in, belt wheel (being equivalent to small gear) 14 links by band and input belt wheel (being equivalent to import gear) 20, this input belt wheel 20 is fixed on the eccentric axon 30.Near the axial substantial middle of eccentric axon 30, be formed with eccentric body shaftgear 28, this eccentric body shaftgear 28 and distribution gear 26 engagements.At this, eccentric axon 30 also also has 2 except diagram, also be formed with eccentric body shaftgear 28 on these eccentric axons 30, respectively with distribution gear 26 engagements.But, on other two eccentric axons 30 beyond the diagram, do not possess input belt wheel 20.In addition, distribution gear 26 is by bearing 80,81 rotations supporting freely.
In gear motor 1, be delivered in the process of all eccentric shafts 30 in the rotation of motor 10, transmit by distribution gear 26.This distribution gear 26 is made of with the small gear 26A that is used for 20 engagements of input gear the gearwheel that is used for small gear 14 engagements, in order to make small gear 14 and directly to mesh from the bigger distribution gear 26 of these small gear 14 axis deviations, the diameter of distribution gear 26 becomes major diameter inevitably even shape also becomes complicated, thereby cost becomes problem.
Summary of the invention
The present invention promptly produces in order to address the above problem a little simultaneously, its problem be to provide low-cost and can realize high reduction speed ratio in connect the engagement type plane table thermoconductivity meter of swing.
Connect the engagement type plane table thermoconductivity meter of swing in of the present invention, solve above-mentioned problem by following structure: the power of input is exported by the external tooth gear deceleration of swing, comprise: input shaft possesses with the input gear of accepting driving force with the small gear outer gearing of the output shaft constant speed of external power supply rotation from this small gear; Input shaft gear is formed on this input shaft; A plurality of eccentric axons possess the eccentric body that is used to make the aforementioned external teeth gearing; The eccentric body shaftgear is formed on 1 in the above-mentioned eccentric axon at least, is used to make this off-centre axon to obtain power; And distribution gear, with above-mentioned input shaft gear and the engagement of above-mentioned eccentric body shaftgear, give above-mentioned a plurality of eccentric body shaftgears with the rotation distribution and transmission of above-mentioned input shaft gear.Above-mentioned input shaft is configured to connect the form of this external tooth gear in the pitch circle inboard of aforementioned external teeth gear.
Owing to adopt this structure, thus can with the input gear when power source obtains power, and slow down from the input shaft gear (passing through distribution gear) of the input shaft two-stage when the eccentric body shaftgear transferring power, can realize high reduction speed ratio.In addition, need not to prepare the distribution gear of big footpath or complicated shape this moment, also do not need necessary above cost.
In addition, comparing above-mentioned input gear with above-mentioned small gear is gearwheel, and comparing above-mentioned eccentric body shaftgear with above-mentioned input shaft gear is gearwheel, thereby also can obtain height (greatly) reduction speed ratio.
The effect of invention
Can provide low-cost and realize high reduction speed ratio in connect the engagement type plane table thermoconductivity meter of swing.
Description of drawings
Fig. 1 is the side cross-sectional view of the gear motor of expression embodiments of the present invention one example.
Fig. 2 is the sectional view along arrow II-II line among Fig. 1.
Fig. 3 is the side cross-sectional view of the gear motor of expression other mode of execution one examples of the present invention.
Fig. 4 is the sectional view along arrow IV-IV line among Fig. 3.
Fig. 5 is the expression side cross-sectional view of the gear motor of other mode of execution one examples more of the present invention.
Fig. 6 is the side cross-sectional view of existing gear motor 1.
Fig. 7 is the side cross-sectional view of existing gear motor 2.
Fig. 8 be existing gear motor 2 ' side cross-sectional view.
Embodiment
Below utilize accompanying drawing, be elaborated about an example of embodiments of the present invention.
Fig. 1 is the side cross-sectional view of the gear motor 100 of expression embodiments of the present invention one example, and Fig. 2 is the sectional view along arrow II-II line among Fig. 1.
Air portion H is formed on the interior week formation of the cylinder flange 131 that connects the 1st, the 2nd carrier 138A, 138B, and this cylinder flange 131 is fixed on the 2nd carrier 138B by mounting screw 129.In addition, accompanying O ring 160 between cylinder flange 131 and the motor fixing body 139 and between cylinder flange 131 and the 2nd carrier 138B, the oiling agent that is sealed in the retarder 101 can not leak into the outside.
Also have, cylinder flange 131 does not directly help transmission of power, thereby, form thinlyyer.Thereby can increase hollow part H, can connect more cable etc.
On the motor shaft 112 of motor 110, possesses small gear 114, so that rotate with motor shaft 112 one (with constant speed).This small gear 114 can for example directly cut out formation on motor shaft 112, also can be the gear that is fixed with as other member.This small gear 114 and diameter are than self big input gear 120 outer gearing.That is, compare with small gear 114, input gear 120 constitutes as gearwheel.Input gear 120 is fixed on the input shaft 122.Input shaft 122 is to connect the form configuration of the 1st carrier 138A and external tooth gear 134.That is, input shaft 122 is configured in the inboard of the pitch circle of external tooth gear 134.Consequently, can will be configured in the pitch circle of internal-gear 136 with the small gear 114 that is fixed on input gear 120 engagements on the input shaft 122.In addition, input shaft 122 freely supports with respect to the rotation of the 1st carrier with bearing 152A by input shaft, also rotates freely supporting with bearing 152B with respect to the 2nd carrier 138B by input shaft.In the present embodiment, input shaft 122 does not connect the 2nd carrier 138B.
In addition, in the axial stage casing of input shaft 122 (between input shaft bearing 152A, the 152B of supporting input shaft 122), be formed with input shaft gear 124 with input shaft 122.This input shaft gear 124 and distribution gear 126 engagements.Distribution gear 126 is including hollow part H, and (passing member: cylindrical body) 131 periphery disposes with quick condition with respect to the cylinder flange that connects this distribution gear.Be not meant in this said " quick condition " and directly support by bearing.
In addition, in the position different with input shaft 122, differing about 120 ° of phase configuration has 3 eccentric axons 130 (with reference to Fig. 2).Axial substantial middle in each eccentric axon 130 partly is formed with eccentric body shaftgear 128, this eccentric body shaftgear 128 and above-mentioned distribution gear 126 engagements.Consequently, form all configuration structures at grade of input shaft gear 124, eccentric body shaftgear 128, distribution gear 126.That is, the position of the radial direction of the distribution gear 126 of quick condition is by above-mentioned input shaft gear 124 and 3 eccentric body shaftgear 128 restrictions.Also have, the diameter of the diameter of eccentric body shaftgear 128 and input shaft gear 124 is in a ratio of big footpath, promptly constitutes as gearwheel.
In addition, at the upside slightly and the downside of eccentric body shaftgear 128, be axial both sides, be formed with the eccentric body 132 that eccentric direction has nothing in common with each other with eccentric axon 130.Also have, each eccentric body 132 cooperates with bearing 133 and external tooth gear 134 (hollow portion) by eccentric body respectively.Promptly the meaning be distribution gear 126 its axially the position of (above-below directions) by 134 restrictions of 2 external tooth gears.
In addition, external tooth gear 134 makes eccentric body 132 cooperate with the hollow portion of self by eccentric body with bearing 133, simultaneously, and with internal tooth 136 engagements of pin shape.The internal tooth 136 of pin shape is counted the number of teeth that is set at external tooth gear 134 a little difference.Also have, in the present embodiment, constitute internal-gear by this internal tooth 136 and housing 140.
Each eccentric axon 130 freely supports with respect to the rotation of the 1st carrier with bearing 154A by eccentric axon, on the other hand, rotates freely supporting with bearing 154B with respect to the 2nd carrier 138B by eccentric axon.
Next, the effect about gear motor 100 describes.
If motor 110 work, then the rotation of motor shaft 112 is delivered to input gear 120 by small gear 114.At this moment, the diameter of comparing input gear 120 with the diameter of small gear 114 is major diameter (gearwheel), and therefore, the rotation of motor shaft 112 is decelerated and is delivered to input shaft 122.If input shaft 122 rotations, then input shaft gear 124 also rotates, and therefore, and then the distribution gear 126 that meshes with input shaft gear 124 is also rotated.At this, owing to compare with the diameter of input shaft gear 124, the diameter of eccentric body shaftgear 128 also is a major diameter (gearwheel), and therefore, the rotation of input shaft 122 is decelerated to eccentric body shaftgear 128 again and transmits.Like this, in the gear motor 100 of present embodiment, by 2 grades of decelerations, the power that slows down with high reduction speed ratio can be continued transmit in the process before the rotation of motor shaft 112 passes to eccentric body 132 to planetary gear speed-reduction portion (eccentric body, external tooth gear, internal tooth).That is, need not to adopt in planetary gear speed-reduction portion and obtain the such structure of high reduction speed ratio by force.
In addition, distribution gear 126 and 3 eccentric body shaftgear 128 engagements, thus link with 3 eccentric axons 130, therefore will give each eccentric axon 130 from the power while distribution and transmission that input shaft 122 transmits.Therefore, can not take place because the backlash skew that causes to the power distribution method of each eccentric axon of the prior art yet.Because the rotation of distribution gear 126, each eccentric axon 130 begin rotation, still, owing on each eccentric axon 130, be formed with eccentric body 132, thereby, by eccentric body 132 eccentric rotations, thereby make external tooth gear 134 swing rotations.At this moment, external tooth gear 134 also meshes with the internal tooth 136 with a little number of teeth difference, thereby external tooth gear 134 carries out a little rotation and almost only swings.This swing composition is by 130 payments of eccentric axon, thereby a little rotation composition of external tooth gear 134 only is delivered to carrier 138 and is output.
Also have, in the present embodiment,, therefore,, and make whole carrier 138 rotations that also comprise motor 110 by the action of gear motor 100 by base station 142 stationary housings 140.
In addition, the distribution gear 126 in the present embodiment is configured in the inside (between the 1st, the 2nd carrier 138A, the 138B) of carrier 138, thereby can design the axial extent of whole device small-sizedly.
In addition, can constitute in the present embodiment, input shaft 122 is configured in the inboard of the pitch circle of external tooth gear 134, also will be configured in the inboard of the pitch circle of internal-gear with the small gear 144 that is fixed on input gear 120 engagements on the input shaft 122.Consequently,, also can on radial direction, constitute whole gear motor even when motor being installed as power source small-sizedly, during running around required space also can be less.In addition, input shaft 122 is bearing on the 1st carrier 138A, the 2nd carrier 138B by bearing 152A, 152B, input shaft gear 124 is formed on the input shaft 122 between this bearing 152A, the 152B, thereby, with so-called dual-supporting state and distribution gear 126 engagements.Thereby input gear 124 and distribution gear can be kept stable engagement.
Next, one example of other mode of executions of the present invention is described.
Fig. 3 is the side cross-sectional view of the gear motor 100A of expression other mode of execution one examples of the present invention, and Fig. 4 is the sectional view along arrow IV-IV line among Fig. 3.
In the present embodiment, and the cylinder flange of formation hollow part H (passing member: 131 forms configurations cylindrical body) with axial perforation distribution gear 126, from cylinder flange 131, support so that this distribution gear 126 can rotate with bearing 127 by 1 distribution gear.Like this, by 1 bearing supporting distribution gear 126, thereby, compare with the front mode of execution, can guarantee rigidity and rotational stabilization are installed reliably, and bearing cost and space can constitute as irreducible minimum.This distribution gear in the present embodiment, is made of a plurality of " roller " with bearing 127.Consequently, the inner peripheral surface of formation cylinder flange 131 outer circumferential faces and distribution gear 126 is brought into play the structure of the effect of the transmission plane that is somebody's turn to do " roller ".In addition, the part of this transmission plane effect of the performance of cylinder flange 131 forms in order to ensure intensity and to have the thickness thicker than other parts (cylinder flange part protuberance 131T).
Also have,, so, have the advantage of the diameter formation larger diameter that can make hollow part H, still, also can constitute by for example ball bearing etc. if as present embodiment, constitute distribution gear bearing 127 as " roller ".If like that, then because the existence of the inner ring that ball bearing possessed, thereby, do not need so big with the intensity of the abutment portion of the bearing of cylinder flange 131 (distribution gear with bearing 127).In addition, in order to ensure the intensity of " roller " transmission plane of cylinder flange 131, except the method for the thickness that changes cylinder flange itself as mentioned above, also can adopt for example surface-treated measure such as high frequency hardening.If like that, then can adopt the diameter of hollow part H biglyyer.
In addition, in the position different with input shaft 122, differing about 120 ° of phase configuration has 3 eccentric axons 130 (with reference to Fig. 4).Axial substantial middle in each eccentric axon 130 partly is formed with eccentric body shaftgear 128, this off-centre axon 128 and above-mentioned distribution gear 126 engagements.Consequently, form input shaft gear 124, eccentric body shaftgear 128, distribution gear 126, distribution gear all configuration structures at grade of bearing 127.According to this structure, the position of the radial direction of distribution gear 126 is under the state that is supported by cylinder flange 131 with bearing 127 by distribution gear, by above-mentioned input shaft gear 124 and 3 eccentric body shaftgears 128 restrictions.
That is, on the same plane of distribution gear 126, dispose input shaft gear 124, eccentric body shaftgear 128, distribution gear with bearing 127, thereby, the power of these distribution gear 126 inputs and from the power of these distribution gear 126 outputs balance at grade.Consequently, can on distribution gear 126, not produce big stall torque.Promptly use 1 distribution gear with bearing 127, also swivel bearing distribution gear 126 accurately.Also have, owing to there is this distribution gear bearing 127, thereby, can bear the uneven radial load (will give the remaining inclined to one side load radially in 128 backs of 3 eccentric body shaftgears) that is applied on the distribution gear 126 from the power distribution that input shaft gear 124 is subjected to, thereby prevent that distribution gear 126 from unnecessary vibration taking place, or the noise that causes by this vibration.
Also have, other constitute with the mode of execution of front same, thereby, get final product with prosign position identical or impartial among the figure is attached, omit repeat specification.
Fig. 5 is an example of expression other mode of executions more of the present invention.
In this mode of execution, the formation of employing is that the axial position of distribution gear is positioned between the 1st carrier 238A (or the 2nd carrier 238B) and the external tooth gear 234 as illustrated in fig. 5.That is, the axial position of distribution gear 226 can be by external tooth gear 234 and carrier 238 restrictions.Particularly be configured under the situation between the 1st carrier 238A and the external tooth gear 234, the weight with external tooth gear 234 of weight can not be applied on the distribution gear 226, therefore, and the reduction of the loss of can seeking to slide.
Also have, other formations among Fig. 5, same with last two mode of executions, thereby to position identical or impartial among the figure, back two attachedly get final product omission repeat specification with prosign.
Also having, in the mode of execution of above-mentioned explanation, show external tooth gear and constitute by 2, still, be not limited thereto, both can be more than 3, also can 1.
In addition, be 3 eccentric axons all be formed with the eccentric body shaftgear, still, be not limited thereto, in 3 eccentric axons, also can have eccentric axon with the driven and eccentric rotation of external tooth gear of swing.Also have, 3 eccentric axons differ 120 ° of phase places mutually and dispose, still, and also can be according to different with it phase configuration.Can form structure according to the change proper phases such as radical of the eccentric axon (being formed with the eccentric axon of eccentric body shaftgear) that disposes.
In addition, do not need to make cable to connect the situation of configuration etc., can not adopt the cylinder flange and adopt solid member.
In addition, also can adopt on motor fixing body swivel bearing to have the axle of small gear and link the mechanism of this and motor shaft with spline etc.
Utilizability on the industry
The present invention is specially adapted to the articular portion of industrial robot.
Claims (11)
1. connect the engagement type plane table thermoconductivity meter of swing in one kind, it is characterized in that,, comprising the output of slowing down of the power of the input external tooth gear by swing:
Input shaft possesses with the input gear of accepting driving force with the small gear outer gearing of the output shaft constant speed of external power supply rotation from this small gear;
Input shaft gear is formed on this input shaft;
A plurality of eccentric axons possess the eccentric body that is used to make the aforementioned external teeth gearing;
The eccentric body shaftgear is formed on 1 in the above-mentioned eccentric axon at least, is used to make this off-centre axon to obtain power; And
Distribution gear with above-mentioned input shaft gear and the engagement of above-mentioned eccentric body shaftgear, is given above-mentioned a plurality of eccentric body shaftgears with the rotation distribution and transmission of above-mentioned input shaft gear,
Above-mentioned input shaft is configured to connect the form of this external tooth gear in the pitch circle inboard of aforementioned external teeth gear.
2. connect the engagement type plane table thermoconductivity meter of swing in according to claim 1, it is characterized in that comparing above-mentioned input gear with above-mentioned small gear is gearwheel, and comparing above-mentioned eccentric body shaftgear with above-mentioned input shaft gear is gearwheel.
3. connect the engagement type plane table thermoconductivity meter of swing in according to claim 1, it is characterized in that, the pitch circle that above-mentioned small gear is configured in the internal-gear that meshes than aforementioned external teeth gear in the inner part.
4. connect the engagement type plane table thermoconductivity meter of swing in according to claim 1, it is characterized in that above-mentioned distribution gear directly is not supported on the bearing, by meshing the position of limiting radial direction with above-mentioned input shaft gear and above-mentioned eccentric body shaftgear.
5. connect the engagement type plane table thermoconductivity meter of swing in according to claim 1, it is characterized in that, above-mentioned input shaft gear, above-mentioned eccentric body shaftgear, and the configuration of above-mentioned distribution gear at grade.
6. connect the engagement type plane table thermoconductivity meter of swing in according to claim 1, it is characterized in that, also comprise
Connect vertically above-mentioned distribution gear passing member,
1 bearing with respect to the rotatably mounted above-mentioned distribution gear of above-mentioned passing member.
7. connect the engagement type plane table thermoconductivity meter of swing in according to claim 6, it is characterized in that, above-mentioned input shaft gear, above-mentioned eccentric body shaftgear, above-mentioned distribution gear and above-mentioned 1 bearing configuration are at grade.
8. connect the engagement type plane table thermoconductivity meter of swing in according to claim 6, it is characterized in that above-mentioned passing member is the cylindrical body of hollow.
9. connect the engagement type plane table thermoconductivity meter of swing in according to claim 6, it is characterized in that above-mentioned bearing is made of a plurality of rollers, the outer circumferential face of above-mentioned passing member and the inner peripheral surface of above-mentioned distribution gear have the function of the transmission plane of this roller.
10. connect the engagement type plane table thermoconductivity meter of swing in according to claim 1, it is characterized in that,
A plurality of aforementioned external teeth gears dispose at axial overlap,
Above-mentioned distribution gear is configured between the aforementioned external teeth gear, thus the position of restrictive axial.
11. connect the engagement type plane table thermoconductivity meter of swing in according to claim 1, it is characterized in that above-mentioned distribution gear is configured in the aforementioned external teeth gear and unloads between the carrier of this external tooth gear rotation composition, thus the position of restrictive axial.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006090112A JP4851826B2 (en) | 2006-03-29 | 2006-03-29 | Inscribed rocking mesh planetary gear reducer |
| JP090112/2006 | 2006-03-29 | ||
| JP103379/2006 | 2006-04-04 |
Related Child Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2008101848690A Division CN101429990B (en) | 2006-03-29 | 2007-03-29 | Reducer |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101046239A CN101046239A (en) | 2007-10-03 |
| CN100523544C true CN100523544C (en) | 2009-08-05 |
Family
ID=38636446
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2008101848690A Active CN101429990B (en) | 2006-03-29 | 2007-03-29 | Reducer |
| CNB2007100890198A Active CN100523544C (en) | 2006-03-29 | 2007-03-29 | Retarder |
Family Applications Before (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2008101848690A Active CN101429990B (en) | 2006-03-29 | 2007-03-29 | Reducer |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP4851826B2 (en) |
| CN (2) | CN101429990B (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4918052B2 (en) * | 2008-02-08 | 2012-04-18 | ナブテスコ株式会社 | Eccentric oscillating gear unit |
| WO2009119737A1 (en) * | 2008-03-28 | 2009-10-01 | ナブテスコ株式会社 | Gear device |
| JP5193072B2 (en) | 2009-01-09 | 2013-05-08 | ナブテスコ株式会社 | Gear transmission |
| JP7316828B2 (en) * | 2019-04-15 | 2023-07-28 | ナブテスコ株式会社 | Decelerator |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2542510B2 (en) * | 1987-03-27 | 1996-10-09 | 住友重機械工業株式会社 | Gearbox with planetary gear mechanism |
| JP3545995B2 (en) * | 2000-06-12 | 2004-07-21 | ファナック株式会社 | Robot joint structure |
| JP3688230B2 (en) * | 2001-08-23 | 2005-08-24 | ナブテスコ株式会社 | Eccentric differential reducer |
| JP2004270846A (en) * | 2003-03-10 | 2004-09-30 | Ts Corporation | Eccentrically swinging reduction gear, rotary drive device provided therewith and container provided with the rotary drive device |
| JP4312484B2 (en) * | 2003-03-26 | 2009-08-12 | 住友重機械工業株式会社 | Swing intermeshing planetary gear unit |
| JP4267950B2 (en) * | 2003-03-28 | 2009-05-27 | 住友重機械工業株式会社 | Internal gear swing type intermeshing planetary gear unit |
-
2006
- 2006-03-29 JP JP2006090112A patent/JP4851826B2/en active Active
-
2007
- 2007-03-29 CN CN2008101848690A patent/CN101429990B/en active Active
- 2007-03-29 CN CNB2007100890198A patent/CN100523544C/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CN101046239A (en) | 2007-10-03 |
| CN101429990A (en) | 2009-05-13 |
| CN101429990B (en) | 2011-05-11 |
| JP4851826B2 (en) | 2012-01-11 |
| JP2007263254A (en) | 2007-10-11 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102472367B (en) | Planetary gear mechanism | |
| CN204828503U (en) | Double pendulum line RV reduction gear for robot | |
| CN101251166B (en) | Oscillating internally meshing planetary gear system | |
| CN107420528B (en) | A kind of cycloid planetary speed reducer, mechanical equipment tooling | |
| JP5533194B2 (en) | Transmission gear unit | |
| CN102472368A (en) | Planetary gear mechanism | |
| CN100523544C (en) | Retarder | |
| JP2542510B2 (en) | Gearbox with planetary gear mechanism | |
| CN106931081A (en) | A kind of robot high-accuracy cycloid difference tooth reductor | |
| CN104747659A (en) | Speed reducer for driving window curtain or door curtain | |
| CN100458217C (en) | Single inputting and double outputting planetary speed reducer | |
| CN100439750C (en) | Pin gear cycloid gear driving device and speed reducer thereof | |
| CN103206491A (en) | Speed reducer | |
| CN102927207B (en) | A kind of zero back clearance planetary transmission speed reducer | |
| CN108591405A (en) | A kind of precision joint type 2-level reducer | |
| CN102141118B (en) | Differential speed reducer | |
| JP7304717B2 (en) | Transmission device | |
| CN104832602B (en) | A kind of power output device of more bent axle cycloid speed reducers | |
| CN109578540A (en) | A kind of straight-tooth planetary gear ball Combined speed reducer | |
| JP2017154241A (en) | Joint driving structure of robot | |
| CN202833877U (en) | Zero-backlash planetary transmission reduction device | |
| CN104964004A (en) | Industrial robot RV speed reducer | |
| CN201110084Y (en) | Drive device and vehicle glass elevator containing the drive device | |
| CN100526677C (en) | Mechanical reduction gear and rim motor including the same | |
| CN107044511A (en) | A kind of robot poor tooth reductor of cycloid |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |