CN1163364A - Planetary speed reducer - Google Patents
Planetary speed reducer Download PDFInfo
- Publication number
- CN1163364A CN1163364A CN 96116899 CN96116899A CN1163364A CN 1163364 A CN1163364 A CN 1163364A CN 96116899 CN96116899 CN 96116899 CN 96116899 A CN96116899 A CN 96116899A CN 1163364 A CN1163364 A CN 1163364A
- Authority
- CN
- China
- Prior art keywords
- bearing
- ring gear
- equates
- planet wheel
- wheel
- 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.)
- Pending
Links
Abstract
In the two-stage planetary speed reducer with pinshaft output mechanism, the two ends of pinshaft are connected separately to two planetary gears, the third planetary gear has through hole for the pinshaft to pass through without contact, the pinshaft as output element operates without work loss, and the input shaft is a dynamically and statically balanced shafting. It has two non-load bearings and its speed ratio is in the range of 11-15,000, its efficiency may reach 97% and is 80% at the speed ratio of 4,000, and its power may reach 5,000 KW.
Description
What the present invention relates to is a kind of twin-stage planetary speed reducer, particularly a kind of NN type twin-stage planetary speed reducer with two internal gears, wherein, ring gear 10 in the first order planetary gear train is for being consolidated in the meront on the housing, be meshed with ring gear 10, and be in each other 180 ° of locational planet wheels 9 and 18 and be bearing in eccentric wheel 11 and 17 that offset equates separately separately on the bearing 14 and 15 outer ring of outer rim, ring gear 4 in the planetary gear train of the second level is as the movement parts of output element, ring gear 4 is the integral body with identical axle center with output shaft 1, be meshed with ring gear 4, and be in each other 180 ° of locational planet wheels 7 and 8 and be bearing in eccentric wheel 19 and 17 that offset equates separately separately on the bearing 5 and 16 outer ring of outer rim, it is characterized by: being between the secondary planet wheel 7 of same phase and the one-level planet wheel 18 is to be positioned at bearing 5 by a group switching centre circle, 14 outer rim is to planet wheel 7, between 18 the root circle near the average diameter, quantity is more than four and the two ends concrete mutually of the bearing pin 6 that equates of its center angle.Make have on whole one-level planet wheel 9 and the secondary planet wheel 8 that quantity equates with bearing pin 6, center circle equates with the center circle of bearing pin 6, supply and marketing axle 6 do not have separately and connects the hole of passing contiguously, one group of passageway 20.The offset of eccentric wheel 19,17,11 equates that the phase place of eccentric wheel 19,11 is identical, and with 180 ° each other of eccentric wheels 17, the shaft axis conllinear of their common rotational axis and input shaft 12 and output shaft 1.
Principle of the present invention and advantage are that the planet wheel 18 in the first order planetary gear train relies on one group of bearing pin 6 contactlessly to cross hole, passageway 20, moment of torsion and corner are passed to ring gear 4 in the planetary gear train of the second level as the movement parts of output element, ring gear 4 is the integral body with identical axle center with output shaft 1, be meshed with ring gear 4, and be in each other 180 ° of locational planet wheels 7 and 8 and be bearing in eccentric wheel 19 and 17 that offset equates separately separately on the bearing 5 and 16 outer ring of outer rim, it is characterized by: being between the secondary planet wheel 7 of same phase and the one-level planet wheel 18 is to be positioned at bearing 5 by a group switching centre circle, 14 outer rim is to planet wheel 7, between 18 the root circle near the average diameter, quantity is more than four and the two ends concrete mutually of the bearing pin 6 that equates of its center angle.Make have on whole one-level planet wheel 9 and the secondary planet wheel 8 that quantity equates with bearing pin 6, center circle equates with the center circle of bearing pin 6, supply and marketing axle 6 do not have separately and connects the hole of passing contiguously, one group of passageway 20.The offset of eccentric wheel 19,17,11 equates that the phase place of eccentric wheel 19,11 is identical, and with 180 ° each other of eccentric wheels 17, the shaft axis conllinear of their common rotational axis and input shaft 12 and output shaft 1.
Principle of the present invention and advantage are that the planet wheel 18 in the first order planetary gear train relies on one group of bearing pin 6 contactlessly to cross hole, passageway 20, moment of torsion and corner be passed on the second level planet wheel 7, and clearly be a kind of no energy consumption mechanism as the bearing pin 6 of output mechanism.And planet wheel 9 and planet wheel 8 are owing to be an integral body, the moment of torsion between them and the transmission of corner are except that the profile of tooth engagement, also be a kind of no energy consumption output, because the pitch diameter of ring gear 4,10 about equally, so the engaging force of planet wheel 7,8,9,18 also about equally, direction is opposite, because the engaging force of planet wheel 7,18 and planet wheel 8,9 is in each other on 180 ° the position all the time, event is with the block bearing the 3, the 13rd of the input shaft 12 of three eccentric wheels 19,17,11, and a kind of zero carries supporting, this has just reduced cost, has improved transmission efficiency.For ring gear 10, planet wheel 9 and 18 engaging force equal and opposite in direction, direction is opposite, acts on two little Different Plane of distance, form less couple, equally, for ring gear 4, planet wheel 7 and 8 engaging force equal and opposite in direction, direction is opposite, act on two little Different Plane of distance, formed less couple, much smaller as a kind of relatively monolateral engagement of support reaction of the block bearing 2 of ring gear 4 like this.In sum, the present invention's input shaft is that a kind of axle quiet, that dynamic balancing possesses is not need to establish in addition counterweight.
In the prior art, its input bearings at both ends of the 678th page of described NN type little tooth difference speed reducer of volume is being carried the onesize support reaction of engaging force in the mechanical design handbook that Chemical Industry Press published in 82 years, and the bearing of ring gear must carry bigger couple and counter-force, it also must establish counterweight in addition, and these have all limited its adaptability and superiority.And the pin axle type output mechanism shown in this book same page bottom is a kind of wasted work element, the power on this bearing pin of acting on is about the twice of engaging force, and with engaging force one trace-stacking affact and be with on the eccentric rotary arm bearing, the efficiency test of analysis and model machine as calculated, it is described to submit a written statement to a higher authority, few tooth difference speed reducer of pin axle type output mechanism, the bearing pin part wasted work of cycloidal planetary gear speed reducer be about the 10-15% of total output, and the present invention's bearing pin wasted work not.
Zero tooth difference parameter is adopted in the present invention such as the second level, and then its ratio coverage can be from more than the 11-15000, the transmission total efficiency is this 97%-80% between speed ratio 11-4000, so the efficient reduced rate when it increases with speed ratio is little, so can be adapted to high-power, the product development of big speed ratio, this is because the line of contact speed of few tooth difference is very low, the event of 1-2% that its engagement wasted work only accounts for total output.
The present invention's profile of tooth can be adapted to involute less tooth difference profile of tooth, cycloidal-pin wheel profile of tooth and arc toothed, horizontal, the vertical type that can be used for coaxial type by the dress form, transmission power can reach more than the 5000KW, in addition, it also has the advantage of little pitch diameter, big speed ratio, big modulus, high-bearing capacity, high transmission efficiency, as: pitch diameter is about 180mm, and velocity ratio is can the common bluebeard to get the bearing capacity of 6mm modulus at 527 o'clock; As pressing facewidth B=20mm; Basic flexural stress during unit facewidth modulus is that then its output torque can be up to 110Kg-M for the 5Kg/mm2 meter.
The low noise that involute less tooth difference type speed reducer has, LCS is well-known.
Describe optimum implementation of the present invention in detail below in conjunction with accompanying drawing.
Accompanying drawing is assembly figure of the present invention, wherein:
1, output shaft
2, bearing
3, bearing
4, ring gear
5, hold axle
6, bearing pin
7, planet wheel
8, planet wheel
9, planet wheel
10, ring gear
11, eccentric wheel
12, input shaft
13, bearing
14, bearing
15, bearing
16, bearing
17, eccentric wheel
18, planet wheel
19, eccentric wheel
20, hole, passageway
Implement the best approach of the present invention and be to choose the less number of teeth with the common bluebeard must be bigger modulus and bigger bearing capacity, but when the secondary planet train adopts zero tooth difference then the common bluebeard get the little speed ratio of big modulus.The ring gear material can select nitriding steel for use in order to avoid the mill internal tooth operation of the costliness that heat treatment deformation brought.Implementing main lathe of the present invention is: gear hobbing machine, gear shaping machine, upright, crouch, milling machine, lathe, planer and heat treatment installation etc.
Claims (3)
1, a kind of NN type twin-stage planetary speed reducer with two internal gears, wherein the ring gear in the first order planetary gear train 10 is for being consolidated in the static element on the housing, be meshed with ring gear 10, and be in each other 180 ° of locational planet wheels 9 and 18 and be bearing in eccentric wheel 11 and 17 that offset equates separately separately on the bearing 14 and 15 outer ring of outer rim, ring gear 4 in the planetary gear train of the second level is the movement parts as output element, ring gear 4 is the integral body with identical axle center with output shaft 1, be meshed with ring gear 4, and be in each other 180 ° of locational planet wheels 7 and 8 and be bearing in eccentric wheel 19 and 17 that offset equates separately separately on the bearing 5 and 16 outer ring of outer rim, it is characterized by: being between the secondary planet wheel 7 of same phase and the one-level planet wheel 18 is to be positioned at bearing 5 by a group switching centre circle, 14 outer rim is to planet wheel 7, near the average diameter between 18 the root circle, quantity is more than four and the two ends concrete mutually of the bearing pin 6 that equates of its center angle.Make and have on whole one-level planet wheel 9 and the secondary planet wheel 8 that quantity equates with bearing pin 6, center circle equates with the center circle of bearing pin 6, the hole, one group of passageway 20 that supply and marketing axle 6 contactlessly passes separately.
2, it is characterized by according to the described structure of claim 1: profile of tooth is involute less tooth difference type, cycloidal-pin wheel type and arc toothed.
3, it is characterized by according to claim 1,2 described structures: velocity ratio is more than the 11-15000, and power reaches vertical, the horizontal twin-stage planetary speed reducer of 5000KW.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 96116899 CN1163364A (en) | 1996-04-19 | 1996-04-19 | Planetary speed reducer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 96116899 CN1163364A (en) | 1996-04-19 | 1996-04-19 | Planetary speed reducer |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1163364A true CN1163364A (en) | 1997-10-29 |
Family
ID=5123852
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 96116899 Pending CN1163364A (en) | 1996-04-19 | 1996-04-19 | Planetary speed reducer |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1163364A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102581466A (en) * | 2012-02-23 | 2012-07-18 | 西安交通大学 | Two-stage planet wheel control cold-pressure welding device and cold-pressure welding method thereof |
| CN102996780A (en) * | 2012-10-09 | 2013-03-27 | 吴小杰 | Grease lubricated star wheel speed reducer for bearing |
-
1996
- 1996-04-19 CN CN 96116899 patent/CN1163364A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102581466A (en) * | 2012-02-23 | 2012-07-18 | 西安交通大学 | Two-stage planet wheel control cold-pressure welding device and cold-pressure welding method thereof |
| CN102581466B (en) * | 2012-02-23 | 2015-04-15 | 西安交通大学 | Two-stage planet wheel control cold-pressure welding device and cold-pressure welding method thereof |
| CN102996780A (en) * | 2012-10-09 | 2013-03-27 | 吴小杰 | Grease lubricated star wheel speed reducer for bearing |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP0286760B1 (en) | Cycloidal equidistant curved gear transmission mechanism and its device | |
| CN106352024B (en) | A kind of single eccentric short transmission chain retarder | |
| CN207093691U (en) | A kind of cycloidal ball deceleration device and its joint of robot | |
| CN109899478A (en) | A kind of high-precision planet few teeth difference twin-differential deceleration mechanism | |
| CN201177029Y (en) | Planet type few teeth difference decelerator | |
| CN2856582Y (en) | Multi-axis balancing internal circular board small gear tolerence speed reducer | |
| CN210034325U (en) | High-precision planetary small-tooth-difference double-differential speed reducing mechanism | |
| CN2303125Y (en) | Planet speed reducer | |
| CN1163364A (en) | Planetary speed reducer | |
| CN2497108Y (en) | Compound planetary reductor | |
| CN2592959Y (en) | Circle-arc tooth 2K-V planetary reducer | |
| CN200958560Y (en) | Coaxial gear-differential speed reducer | |
| CN214661788U (en) | Base cycloidal speed reducer for industrial heavy-duty robot | |
| CN1024585C (en) | Internally engaged planetary driving machanism with new structure | |
| CN201090682Y (en) | Internal three-cycle speed reducer | |
| CN101117997A (en) | Internal tricyclic decelerator | |
| CN111853168A (en) | Built-in planetary gear reducer | |
| CN1060556C (en) | Cycloidal ball planet speed reducer | |
| CN112780728A (en) | Cylindrical ring groove type double cycloid small tooth difference planetary reducer | |
| CN2085446U (en) | Internal intermeshing planet transmission | |
| CN1016523B (en) | Planetary transmission of circular arc gear engaged with pin gear | |
| CN204852191U (en) | Industrial robot RV reduction gear | |
| CN1721735A (en) | Involute cycloid roller chain planet harmonic composite deceleration transmission mechanism | |
| CN2353244Y (en) | Device for adjusting angle of chair back | |
| CN2414251Y (en) | Speed reducer |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C06 | Publication | ||
| PB01 | Publication | ||
| C01 | Deemed withdrawal of patent application (patent law 1993) | ||
| WD01 | Invention patent application deemed withdrawn after publication |