CN102042369B - Improved planetary reducer - Google Patents
Improved planetary reducer Download PDFInfo
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- CN102042369B CN102042369B CN 201010609468 CN201010609468A CN102042369B CN 102042369 B CN102042369 B CN 102042369B CN 201010609468 CN201010609468 CN 201010609468 CN 201010609468 A CN201010609468 A CN 201010609468A CN 102042369 B CN102042369 B CN 102042369B
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- sun gear
- ring
- planet
- planet carrier
- gear
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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
- F16H1/46—Systems consisting of a plurality of gear trains each with orbital gears, i.e. systems having three or more central gears
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- Engineering & Computer Science (AREA)
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Abstract
The invention relates to the technical field of a planetary reducer, in particular to an improved planetary reducer. The improved planetary reducer is characterized in that sun wheels (22 and 27) and planetary carriers (4 and 14) are in full-floating structures, wherein the planetary carrier (4) and the sun wheel (27) and the planetary carrier (14) and the sun wheel (22) are respectively connected by means of a 30-degree spline self-centering function, and the top of a spline gear end is chamfered by 5-10 degrees; and when a planetary wheel (8 or 16) is engaged with a gear ring (9 or 25), lubrication oil is extruded into a root radial hole (A), is then moved into a diversion port (B) through the circumferential clearance of a roller pin (7 or 17) and the end-surface lateral clearance between the roller pin (7 or 17) and retaining rings (6 and 10 or 15 and 17) and is finally discharged via an axial hole (C), thereby realizing lubrication and heat exchange. Compared with the prior art, the invention has the advantages of simple and novel structure, high power density, fine lubrication, reliable seal, low noise, long service life and high reliability, and can be used in complicated environment and other situations.
Description
[technical field]
The present invention relates to the planetary speed reducer technical field, a kind of specifically improved planetary speed reducer.
[background technique]
Planetary speed reducer is a kind of broad-spectrum industrial products, its performance can compare favourably with other army's grade speed reducer product, the price that technical grade product is but arranged is mainly used in the swirl gear of tower crane, can be used as matching parts again and is used for industries such as lifting, excavation, transportation, building.The main drive mechanism of planetary speed reducer is: planet wheel, sun gear, external toothing. planetary speed reducer is because reasons in structure, single-stage deceleration minimum is 3, maximum generally is no more than 10, common reduction speed ratio is: 3.4.5.6.8.10, speed reducer progression generally is no more than 3, but has the part big retarding than the customization speed reducer 4 grades of decelerations to be arranged.
Domestic patent 200910152356.6 discloses a kind of novel planetary reduction gear, comprises support, nose circle lid, output shaft, input shaft.Bearing and the sealing combination train that constitutes by planet carrier, internal gear, sun gear, planet wheel, planet wheel shaft.It is characterized in that: a machine base body is the uniform solid of rotation of wall thickness, and radiating fin is arranged; B support wall thickness should satisfy formula: T ↓ ［ 2 ］=10.5-1.3 δ ↑ ［ 4 ］ Nm, δ-wall thickness mm with the moment of torsion that acts on support; C internal gear cylindrical spline cooperates with the cylinder internal spline.This novel planetary reduction gear support casting, in light weight, technology capability is good, but planetary speed reducer is applied to occasion, its working life and reliability deficiencies such as heavy load, frequent clockwise and anticlockwise, circumstance complication more.
[summary of the invention]
Be to overcome the deficiencies in the prior art order of the present invention, the planetary speed reducer of a kind of novel structure, long service life, reliable performance is provided.
For achieving the above object, design a kind of improved planetary speed reducer, comprise output shaft 1, first oil sealing 2, output flange 3, first planet carrier 4, first planet axis 5, first back-up ring 6, first needle roller 7, first planet wheel 8, first gear ring 9, second back-up ring 10, subplate 11, adpting flange 12, second planet axis 13, second planet carrier 14, the 3rd back-up ring 15, second planet wheel 16, second needle roller 17, the 4th back-up ring 18, input shaft 19, second oil sealing 20, bearing 21, first sun gear 22, input flange 23, elastic cylindrical pin 24, second gear ring 25, spring sheet 26, second sun gear 27, the 3rd gear ring 28, articulation hole bolt 29, spring sheet 30, it is characterized in that first sun gear 22 and second sun gear 27, first planet carrier 4 and second planet carrier 14 are the full floating structure, first planet carrier 4 and second sun gear 27, second planet carrier 14 adopts 30 degree spline self contering functions to be connected respectively with first sun gear 22, spline gear end top chamfer 5 ~ 10 degree, make it have the aligning effect, first planet carrier 4 is low speed and simple beam split-type structural, first planet carrier 4 and subplate 11 adopt articulation hole to be connected as a single entity with bolt, first planet carrier 4 adopts steel material, subplate 11 adopts the magnesium iron casting, first planet wheel 8, bearing outer ring is made in 16 internal controls of second planet wheel, first planet axis 5, the full needle construction that second planet axis 13 is made bearing inner race adapts to the heavy load operating mode, first planet wheel 8, second planet wheel 16 and first gear ring 9, during 25 engagements of second gear ring, extruding lubricant oil enters tooth root radial hole A by first needle roller 7, second needle roller, 17 circumferential clearances, through first needle roller 7, second needle roller 17 and first back-up ring 6 and second back-up ring 10, the end face sideshake of the 3rd back-up ring 15 and the 4th back-up ring 18 enters flow-guiding mouth B,, realize planet wheel friction lubricating and heat exchange after axial bore C discharges; Second sun gear 27, first sun gear 22 and first planet wheel 8, during 16 engagements of second planet wheel, extruding lubricant oil enters tooth root radial hole F and enters axial bore E, row is to the rubbing surface of spring sheet 30 and second sun gear 27 and the spring sheet 26 and first sun gear 22, under centrifugal action, through spring sheet 30 and second sun gear 27 and spring sheet 26 and the discharge of first sun gear, 22 sideshakes, realize the secondary lubricated and heat exchange of sun gear end-face friction, when sun gear and planet carrier relative movement, be provided with the adjustment structure, input shaft and output shaft are provided with sealing configuration, impact for the buffering counter-rotating, be provided with the second elastic ring pin 28, first elastic cylindrical pin 24 is strengthened;
When sun gear and planet carrier relative movement, be provided with the adjustment structure, axial deflection takes place, spring sheet 30,26 flexible self adaption axial dimensions change, and avoid axially killing, and make the light coadaptation mutually of sun gear and planet carrier adjustment;
The input shaft sealing configuration adopts band sealed bearing and a rotation lip oil sealing;
The output shaft sealing configuration adopts the dual-oil seal design, and junction plane adopts the end face seal with O ring;
Be applied to the gear ring standard pitch diameter less than 500, on the Gear Planet Transmission structure of input speed 3000rpm, output torque 100000N.m.
The present invention is compared with prior art, and is simple in structure, novel, the specific power height, and lubricated good, sealing is reliable, and noise is low, long service life, the reliability height can be applicable to occasions such as circumstance complication.
[description of drawings]
Fig. 1 is a structural representation of the present invention;
Fig. 2 is a partial schematic diagram of the present invention;
Fig. 3 is sun gear of the present invention and planet carrier motion state diagram;
Drawings 1 output shaft 2. First Seal 3. Output flange 4. The first carrier 5. First planetary shaft 6 The first ring 7. Section a needle 8. first planetary gear 9 first ring gear 10 second ring 11. deputy board 12. connection flange 13 second planetary shaft 14. the second carrier 15. third ring 16. second planetary wheel 17 second roller 18 second ring 19. input shaft 20 second seal 21. bearing 22 first sun gear 23. input flange 24. first elastic cylindrical pin 25 second ring gear 26 first elastic pieces 27. No. two sun gear 28 second elastic cylindrical pin 29. articulation hole bolt 30 second elastic piece.
[embodiment]
The invention will be further described below in conjunction with drawings and the specific embodiments, and this manufacturing technology is fully aware of to the art technology people.
Referring to Fig. 1, consider effect of load balancing mechanism, adopt sun gear 22/27, planet carrier 4/14 full floating utilizes 30 degree spline self contering functions to connect, and spline increment top chamfer 5 ~ 10 degree make it have certain aligning effect, and spline is fit to the heavy load operating mode simultaneously.
The planet carrier design
Consider the planet wheel assembling, slow speed turbine stage adopts the simply supported beam split-type design, and level adopts the overhang design at a high speed
The A slow speed turbine stage: planet carrier 4 and subplate 11 adopt articulation hole to be connected as a single entity with bolt; Planet carrier 4 adopts steel material, and subplate 11 adopts the magnesium iron casting, adapts to the heavy load operating mode.
B is level at a high speed: planet carrier 14 adopts steel material, the overhang design.Avoid dynamic balance weight, satisfy economic performance.
Design bearing
Adopt full pin design, planet wheel 8/16 endoporus is made bearing outer ring, and planet axis 5/13 is done the inner ring integrated design, compact structure, and technology, economic performance are good, adapt to the heavy load operating mode.
Lubrication Design
Referring to Fig. 2 planet wheel friction pair:
Planet wheel 8/16 is during with gear ring 9/25 engagement, and extruding lubricant oil enters tooth root radial hole A by needle roller 7/17 circumferential clearance, enters flow-guiding mouth B through the end face sideshake of needle roller 7/17 and back-up ring 6,10/15,17, after axial bore C discharges, realizes lubricated and heat exchange.
Referring to Fig. 3 sun gear end face friction pair:
When sun gear 27/22 meshes with planet wheel 8/16, extruding lubricant oil enters tooth root radial hole F and enters axial bore E, row is to the rubbing surface of spring sheet 30 with sun gear 27 and spring sheet 26 and sun gear 22, under centrifugal action, discharge with sun gear 22 sideshakes through spring sheet 30 and sun gear 27 and spring sheet 26, realize lubricated and heat exchange.When sun gear and planet carrier relative movement, axial deflection takes place in the coadaptation adjustment, becomes monolateral and contacts situation and form sideshake with spring sheet is capable.
The axial restraint design:
When sun gear and planet carrier relative movement, axial deflection takes place in the coadaptation adjustment, and design flexibility sheet 30/26 flexible self adaption axial dimension changes, and avoids axially killing, and makes the light coadaptation mutually of sun gear and planet carrier adjustment.
Seal Design:
Input shaft adopts band sealed bearing and a rotation lip oil sealing, and output shaft adopts the dual-oil seal design, and junction plane adopts the end face seal with O ring.
Design is impacted in clockwise and anticlockwise:
Planetary speed reducer specific power height, the frictional force that the tension of gear ring circumferential arrangement bolt produces is not enough to overcome the relative movement of part, and design flexibility straight pin 28/24 is strengthened and is cushioned counter-rotating and impact.
The present invention can be applicable to the gear ring standard pitch diameter less than 500, the design of input speed 3000rpm, output torque 100000N.m.
Claims (3)
1. improved planetary speed reducer, comprise output shaft (1), first oil sealing (2), output flange (3), first planet carrier (4), first planet axis (5), first back-up ring (6), first needle roller (7), first planet wheel (8), first gear ring (9), second back-up ring (10), subplate (11), adpting flange (12), second planet axis (13), second planet carrier (14), the 3rd back-up ring (15), second planet wheel (16), second needle roller (17), the 4th back-up ring (18), input shaft (19), second oil sealing (20), bearing (21), first sun gear (22), input flange (23), first elastic cylindrical pin (24), second gear ring (25), first spring sheet (26), second sun gear (27), second elastic cylindrical pin (28), articulation hole bolt (29), second spring sheet (30), it is characterized in that first sun gear (22) and second sun gear (27), first planet carrier (4) and second planet carrier (14) are the full floating structure, first planet carrier (4) and second sun gear (27), second planet carrier (14) adopts 30 degree spline self contering functions to be connected respectively with first sun gear (22), spline gear end top chamfer 5 ~ 10 degree, make it have the aligning effect, first planet carrier (4) is a slow speed turbine stage simple beam split-type structural, first planet carrier (4) and subplate (11) adopt articulation hole to be connected as a single entity with bolt, first planet carrier (4) adopts steel material, subplate (11) adopts the magnesium iron casting, second planet carrier (14) adopts steel material, the overhang design, first planet wheel (8), second planet wheel (16) endoporus is made bearing outer ring, first planet axis (5), the full needle construction that second planet axis (13) is made bearing inner race adapts to the heavy load operating mode, first planet wheel (8), second planet wheel (16) and first gear ring (9), during second gear ring (25) engagement, extruding lubricant oil enters tooth root radial hole (A) by first needle roller (7), second needle roller (17) circumferential clearance, through first needle roller (7), second needle roller (17) and first back-up ring (6) and second back-up ring (10), the end face sideshake of the 3rd back-up ring (15) and the 4th back-up ring (18) enters flow-guiding mouth (B),, realize planet wheel friction lubricating and heat exchange after axial bore (C) is discharged; Second sun gear (27), first sun gear (22) and first planet wheel (8), during second planet wheel (16) engagement, extruding lubricant oil enters tooth root radial hole (F) and enters axial bore (E), row is to the rubbing surface of second spring sheet (30) with second sun gear (27) and first spring sheet (26) and first sun gear (22), under centrifugal action, discharge with first sun gear (22) sideshake through second spring sheet (30) and second sun gear (27) and first spring sheet (26), realize the secondary lubricated and heat exchange of sun gear end-face friction, when sun gear and planet carrier relative movement, be provided with the adjustment structure, axial deflection takes place, second spring sheet (30), the flexible self adaption axial dimension of first spring sheet (26) changes, avoid axially killing, make the light coadaptation mutually of sun gear and planet carrier adjustment, input shaft and output shaft are provided with sealing configuration, impact for the buffering counter-rotating, be provided with second elastic cylindrical pin (28), first elastic cylindrical pin (24) is strengthened.
2. a kind of improved planetary speed reducer as claimed in claim 1 is characterized in that the input shaft sealing configuration adopts band sealed bearing and a rotation lip oil sealing.
3. a kind of improved planetary speed reducer as claimed in claim 1 is characterized in that the output shaft sealing configuration adopts the dual-oil seal design, and junction plane adopts the end face seal with O ring.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201010609468 CN102042369B (en) | 2010-12-28 | 2010-12-28 | Improved planetary reducer |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201010609468 CN102042369B (en) | 2010-12-28 | 2010-12-28 | Improved planetary reducer |
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| Publication Number | Publication Date |
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| CN102042369A CN102042369A (en) | 2011-05-04 |
| CN102042369B true CN102042369B (en) | 2013-07-31 |
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| CN 201010609468 Active CN102042369B (en) | 2010-12-28 | 2010-12-28 | Improved planetary reducer |
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Families Citing this family (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102287487A (en) * | 2011-08-12 | 2011-12-21 | 中国煤炭科工集团太原研究院 | Planetary transmission device with high reliability and no bearing |
| CN103089931B (en) * | 2013-02-05 | 2016-02-10 | 重庆市璧山爱华有限责任公司 | Non-maintaining vertical-type planetary gear reduction unit |
| CN103148200B (en) * | 2013-03-19 | 2016-12-28 | 湘潭大学 | A kind of epicyclic gearbox shock resistance flexible connecting structure |
| CN103192941B (en) * | 2013-04-12 | 2015-04-08 | 江苏飞马动力科技有限公司 | Suspension internal gear structure for reducing noise of high-speed motor of electric bicycle |
| CN107985927A (en) * | 2017-11-30 | 2018-05-04 | 台邦电机工业集团有限公司 | A kind of planetary reduction gear formula motorized pulleys |
| CN107859715B (en) * | 2017-12-07 | 2023-08-15 | 东莞市领亚自动化科技有限公司 | Novel planetary gear reducer |
| CN113175520B (en) * | 2021-04-30 | 2023-04-28 | 东风商用车有限公司 | Lubrication heat dissipation structure of sun gear |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1030611A (en) * | 1962-02-10 | 1966-05-25 | Rheinstahl Huettenwerke Ag | Improvements in spur-wheel gearing |
| CN2526593Y (en) * | 2001-09-19 | 2002-12-18 | 张宪英 | Differential mechanism |
| CN2665457Y (en) * | 2003-12-05 | 2004-12-22 | 长春市英光机电发展有限责任公司 | Automatic aligning differential device |
| CN201925419U (en) * | 2010-12-28 | 2011-08-10 | 上海合纵重工机械有限公司 | Improved planetary reducer |
-
2010
- 2010-12-28 CN CN 201010609468 patent/CN102042369B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1030611A (en) * | 1962-02-10 | 1966-05-25 | Rheinstahl Huettenwerke Ag | Improvements in spur-wheel gearing |
| CN2526593Y (en) * | 2001-09-19 | 2002-12-18 | 张宪英 | Differential mechanism |
| CN2665457Y (en) * | 2003-12-05 | 2004-12-22 | 长春市英光机电发展有限责任公司 | Automatic aligning differential device |
| CN201925419U (en) * | 2010-12-28 | 2011-08-10 | 上海合纵重工机械有限公司 | Improved planetary reducer |
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| CN102042369A (en) | 2011-05-04 |
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