CN108488335B - speed variator based on small tooth difference planetary gear - Google Patents
speed variator based on small tooth difference planetary gear Download PDFInfo
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- CN108488335B CN108488335B CN201810724518.8A CN201810724518A CN108488335B CN 108488335 B CN108488335 B CN 108488335B CN 201810724518 A CN201810724518 A CN 201810724518A CN 108488335 B CN108488335 B CN 108488335B
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- planetary 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
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/70—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
Abstract
A speed changer based on a small tooth difference planetary gear comprises a shell, a crankshaft arranged in the shell, differential small tooth difference planetary gears which are connected in series on the crankshaft in multiple stages, a power input shaft and a power output shaft, wherein adjacent differential small tooth difference planetary gears are connected through a crank structure, the differential small tooth difference planetary gears are rotationally connected with the crankshaft through bearings, the power input shaft is rotationally connected with the shell, the end of the power input shaft is located outside the shell, the other end is connected with the crankshaft through a clutch and a second clutch and is connected with an inner gear ring of a -stage differential small tooth difference planetary gear, a brake corresponding to an inner gear ring of the multi-stage differential small tooth difference planetary gear is arranged on the shell, the power output shaft is rotationally connected with the shell, the end of the power output shaft is connected with an outer gear cycloidal gear of the last -stage differential small tooth difference planetary gear through a second crank structure, and the other end of the power output shaft is located outside the shell.
Description
Technical Field
The invention relates to transmission mechanisms, in particular to a transmission based on a planetary gear with small tooth difference.
Background
The gear transmission is mechanical devices which are quite in application, and with the high-speed development of modern industry, the level of mechanization and automation is continuously improved, the requirement on the transmission is higher and higher, the size is small, the weight is light, the speed change range is large, the efficiency is high, the bearing capacity is strong, and the service life is long, so that the development direction of the modern transmission is formed.
The small teeth difference planetary gear transmission technology developed by is gradually developed from the sixties of the twentieth century, and has the advantages of (1) large transmission ratio, within the range of 10-1000 for single-stage small teeth difference planetary gear transmission mechanism, (2) compact structure, small size, and obviously reduced volume and mass compared with the common cylindrical gear transmission with the same transmission ratio and the same power, (3) high transmission efficiency, within the reasonable design, manufacture and assembly, the small teeth difference planetary gear transmission mechanism efficiency is about 0.8-0.94, and (4) high overload and impact bearing performance and long service life, and the large-deflection internal gear pair is adopted, so that the contact strength and bending strength are improved, and the service life can be greatly prolonged.
However, most of the existing planetary gear transmission technologies with small tooth difference are applied to speed reducers, and cannot simply realize step-by-step speed change while realizing large transmission ratio, so that -step advance and application of the technology are limited, for example, the technology can not realize multi-step speed regulation in Chinese patent application No. CN 201510827603.3.
Disclosure of Invention
Aiming at the defects in the prior art, the invention aims to provide transmissions based on planetary gears with small tooth difference, and the transmissions can be subjected to multi-stage speed regulation.
The technical scheme includes that speed changers based on the small-tooth-difference planetary gears comprise a shell, a crankshaft arranged in the shell, and multiple stages of differential small-tooth-difference planetary gears connected in series on the crankshaft, wherein adjacent differential small-tooth-difference planetary gears are connected through a crank structure, the differential small-tooth-difference planetary gears are rotatably connected with the crankshaft through bearings, the speed changer further comprises a power input shaft and a power output shaft, the power input shaft is rotatably connected with the shell, the end of the power input shaft is located outside the shell, the other end is respectively connected with the crankshaft and inner gear rings of a -stage differential small-tooth-difference planetary gear through a clutch and a second clutch, a brake corresponding to the inner gear ring of the multi-stage differential small-tooth-difference planetary gear is arranged on the shell, the power output shaft is rotatably connected with the shell, the end of the power output shaft is connected with an outer gear cycloidal gear of a last -stage small-tooth-difference planetary gear through a second crank structure, and the other end of the power output shaft is located.
The crank structure and the second crank structure both comprise cylindrical connecting columns, circular shaft holes corresponding to the cylindrical connecting columns are formed in outer cycloidal gears of differential type few-tooth-difference planetary gears, the cylindrical connecting column of the crank structure is vertically arranged on the side faces of inner gear rings of rear -level differential type few-tooth-difference planetary gears in adjacent differential type few-tooth-difference planetary gears, the cylindrical connecting column of the crank structure is inserted into the circular shaft holes of the outer cycloidal gears on front -level differential type few-tooth-difference planetary gears in the adjacent differential type few-tooth-difference planetary gears, the cylindrical connecting column of the crank structure and the circular shaft holes of the outer cycloidal gears are eccentrically arranged, the distance between the axis of the cylindrical connecting column of the crank structure and the axis of the circular shaft holes is a, the distance between the circle center of the outer cycloidal gears of the differential type few-tooth-difference planetary gears and the inner gear rings of the outer cycloidal gears of the differential type few-tooth-difference planetary gears is b, a and b are equal, the cylindrical connecting column of the second crank structure is fixedly arranged at the end part of a power output shaft, and the cylindrical connecting column of the crank structure is inserted into.
The th clutch and the second clutch are both multi-plate hydraulic friction clutches.
The brake is a pneumatic tire brake.
The casing includes controls both ends open-ended cylindrical barrel, and both ends lid is equipped with "canopy" form end cover about the cylindrical barrel.
The umbrella cover-shaped end cover is connected with the cylindrical barrel through a bolt.
The differential type planetary gear with less tooth difference is three-stage, and the differential type planetary gear with less tooth difference at each stage has the same structure.
An outer tooth cycloid gear of the -level differential type small tooth difference planetary gear and an outer tooth cycloid gear of the third-level differential type small tooth difference planetary gear are eccentric downwards, and an outer tooth cycloid gear of the second-level differential type small tooth difference planetary gear is eccentric upwards.
The invention has compact structure and small volume, and can realize multi-stage speed regulation by matching the th clutch, the second clutch and the brake, thereby meeting different speed requirements.
Drawings
FIG. 1 is a schematic structural view of the present invention;
FIG. 2 is a cross-sectional view of the present invention;
FIG. 3 is a structural diagram of the crank of the invention;
fig. 4 is a schematic diagram of the structure of the present invention.
Detailed Description
As shown in fig. 1 to 4, transmission based on the differential planetary gear comprises a shell, a crankshaft 1 arranged in the shell, and three differential planetary gears connected in series on the crankshaft 1, wherein each differential planetary gear has the same structure, adjacent differential planetary gears are connected through a crank structure, the differential planetary gears are rotatably connected with the crankshaft 1 through bearings, the transmission further comprises a power input shaft 2 and a power output shaft 3, the power input shaft 2 is rotatably connected with the shell, the end of the power input shaft 2 is located outside the shell, the end of the power output shaft is respectively connected with the crankshaft 1 and the inner gear ring 6 of the differential planetary gear of the third stage through a clutch 4 and a second clutch 5, the shell is provided with three brakes 7 corresponding to the inner gear ring of the differential planetary gear, the power output shaft 3 is rotatably connected with the shell, the end of the power output shaft 3 is connected with the cycloidal gear 8 of the differential planetary gear of the third stage planetary gear through a third crank structure, and the other end of the shell is located outside the shell.
The crank structure and the second crank structure both comprise cylindrical connecting columns 9, circular shaft holes 10 corresponding to the cylindrical connecting columns 9 are arranged on outer tooth cycloidal gears of three-stage differential type small-tooth-difference planetary gears, the cylindrical connecting columns 9 of the crank structure are vertically arranged on the side faces of inner gear rings of rear -stage differential type small-tooth-difference planetary gears in adjacent differential type small-tooth-difference planetary gears, the cylindrical connecting columns 9 of the crank structure are inserted into the circular shaft holes 10 of the outer tooth cycloidal gears on front -stage differential type small-tooth-difference planetary gears in adjacent differential type small-tooth-difference planetary gears, the cylindrical connecting columns 9 of the crank structure and the circular shaft holes 10 of the outer tooth cycloidal gears are eccentrically arranged, the distance between the axis of the cylindrical connecting columns 9 of the crank structure and the axis of the circular shaft holes 10 is a, the distance between the centers of the outer tooth cycloidal gears of the differential type small-tooth-difference planetary gears and the centers of the inner gear rings of the differential type small-tooth-difference planetary gears is b, a distance between a circle centers of the cylindrical connecting columns 9 of the second crank structure is fixedly arranged at the end portion of the power output shaft 3, the cylindrical connecting columns of the second crank structure is inserted into the cylindrical connecting columns 9 of the third-stage differential.
The th clutch 4 and the second clutch 5 are both multi-plate hydraulic friction clutches, and the brake 7 is a pneumatic tire brake.
The shell comprises a cylindrical barrel body 11 with openings at the left end and the right end, and umbrella cover-shaped end covers 12 are arranged at the left end and the right end of the cylindrical barrel body 11. The umbrella cover-shaped end cover 12 is connected with the cylindrical barrel 11 through bolts, and is convenient to detach and install.
The th stage differential type small tooth difference planetary gear external tooth cycloid wheel 13 and the third stage differential type small tooth difference planetary gear external tooth cycloid wheel 8, the second stage differential type small tooth difference planetary gear external tooth cycloid wheel 14 is eccentric upwards, and the vibration of the device can be reduced when the device works.
The tooth numbers of external tooth cycloid gears of three differential type small tooth difference planetary gears which are connected in series on the crankshaft 1 are the same and are all z1(ii) a The teeth number of the inner gear rings of the differential type small-tooth-difference planetary gears connected in series on the crankshaft 1 is the same, and all the inner gear rings are z2Wherein z is2And z1The difference of (a) is 1, 2, 3 or 4, while the module of all gears is the same.
Example 1
z1=103, coefficient of variation x1=1.013； z2=104, coefficient of variation x2= 1.784. The input rotating speed of the power input shaft 2 is 2930 r/min.
When the th clutch 4 and the brake 7 corresponding to the third stage differential type small tooth difference planetary gear are started simultaneously, the th gear of the device is achieved, the power input shaft 2 is connected with the crankshaft 1, the rotating speed of the crankshaft 1 is the same as that of the power input shaft 2, the inner gear ring 15 of the third stage differential type small tooth difference planetary gear is locked with the cylindrical barrel 11, the outer cycloidal gear 8 of the third stage differential type small tooth difference planetary gear revolves along with the crankshaft 1 in the inner gear ring 15 of the third stage differential type small tooth difference planetary gear, meanwhile, the outer cycloidal gear 8 of the third stage differential type small tooth difference planetary gear generates autorotation, the power output shaft 3 is driven to rotate through the second crank structure, the rotating speed of the power output shaft 3 is the same as that of the autorotation of the outer cycloidal gear 8 of the third stage differential type small tooth difference planetary gear, the transmission ratio is that the minus sign represents that the rotating direction of the power output shaft 3 is opposite to that of the power input shaft 2, and the rotating speed of the.
When the clutch 4 and the brake 7 corresponding to the second stage differential type small tooth difference planetary gear are started simultaneously, the second stage of the device is provided, the power input shaft 2 is connected with the crankshaft 1, the rotating speed of the crankshaft 1 is the same as that of the power input shaft 2, the inner gear ring 16 of the second stage differential type small tooth difference planetary gear is locked with the cylindrical barrel 11, the outer cycloidal gear 14 of the second stage differential type small tooth difference planetary gear revolves under the driving of the crankshaft 1, because the inner gear ring 16 of the second stage differential type small tooth difference planetary gear is fixed, the outer cycloidal gear 14 of the second stage differential type small tooth difference planetary gear also rotates while revolving, the outer cycloidal gear 14 of the second stage differential type small tooth difference planetary gear drives the outer gear ring 15 of the third stage differential type small tooth difference planetary gear to rotate through a third crank structure, the outer gear ring 15 of the third stage differential type small tooth difference planetary gear drives the outer gear ring 15 of the third stage differential type small tooth difference planetary gear to drive the outer cycloidal gear 8 of the third stage differential type small tooth difference planetary gear to rotate through the second crank structure, the outer gear 8 of the third stage differential type small tooth difference planetary gear drives the inner gear to rotate through the second crank structure.
The third gear of the device is the same when the th clutch 4 and the brake 7 corresponding to the th differential small-tooth-difference planetary gear are started simultaneously, the power input shaft 2 is connected with the crankshaft 1, the rotating speed of the crankshaft 1 is the same as that of the power input shaft 2, the inner gear ring 6 of the th differential small-tooth-difference planetary gear is locked with the cylindrical barrel 11, according to the working principle of the second gear, the th differential small-tooth-difference planetary gear outer-tooth cycloidal gear 13 revolves and rotates under the action of the crankshaft 1, the th differential small-tooth-difference planetary gear outer-tooth cycloidal gear 13 drives the power output shaft 3 to rotate through the second stage differential small-tooth-difference planetary gear and the third stage differential small-tooth-difference planetary gear in sequence, and the transmission ratio is that the rotating speed of the power output shaft 3 is-86.2 r/min.
When the second clutch 5 and the brake 7 corresponding to the third-stage differential type small tooth difference planetary gear are started simultaneously, the fourth gear of the device is set, the power input shaft 2 is connected with the inner gear ring 6 of the -stage differential type small tooth difference planetary gear, the rotating speed of the inner gear ring 6 of the -stage differential type small tooth difference planetary gear is the same as that of the power input shaft 2, the outer gear cycloidal gear 8 of the third-stage differential type small tooth difference planetary gear drives the power output shaft 3 to rotate, and the transmission ratio is shown in the formula, wherein the formula is from the cymbal and cydic gear transmission design [ M ]. Beijing: chemical industry Press, 2014, and the rotating speed of the power output shaft 3 is-1486.4 r/min.
When the second clutch 5 and the brake 7 corresponding to the second stage differential type small tooth difference planetary gear are started simultaneously, the fifth gear of the device is set, the power input shaft 2 is connected with the inner gear ring 6 of the stage differential type small tooth difference planetary gear, the rotating speed of the inner gear ring 6 of the stage differential type small tooth difference planetary gear is the same as that of the power input shaft 2, the outer cycloidal gear 13 of the stage differential type small tooth difference planetary gear rotates and revolves under the action of the inner gear ring 6 of the stage differential type small tooth difference planetary gear, the outer cycloidal gear 13 of the stage differential type small tooth difference planetary gear drives the crankshaft 1 to rotate while revolving, the outer cycloidal gear 14 of the second stage differential type small tooth difference planetary gear revolves and simultaneously rotates under the driving of the crankshaft 1, and the outer cycloidal gear 14 of the second stage differential type small tooth difference planetary gear drives the power output shaft 3 to rotate according to the working principle of the second gear, and the rotating speed of the power output shaft 3 is-5888.4 r/min.
The th clutch 4 and the second clutch 5 are started simultaneously, the power input shaft 2 drives the ring gear 6 of the th differential type small tooth difference planetary gear and the crankshaft 1 to synchronously rotate, at the moment, the three-level differential type small tooth difference planetary gear as integers synchronously rotate along with the power input shaft 2 and simultaneously drive the power output shaft 3 to rotate, the transmission ratio is 1, and the rotating speed of the power output shaft 3 is 2930 r/min.
Claims (8)
- The transmission based on the small-tooth-difference planetary gears comprises a shell, a crankshaft arranged in the shell and a plurality of differential small-tooth-difference planetary gears connected in series on the crankshaft in a multistage mode, wherein adjacent differential small-tooth-difference planetary gears are connected through a crank structure, and the differential small-tooth-difference planetary gears are in rotary connection with the crankshaft through bearings.
- 2. The transmission based on planetary gears with small tooth difference as claimed in claim 1, wherein the crank structure and the second crank structure both include cylindrical connecting columns, the outer cycloidal gear of the differential planetary gear with small tooth difference is provided with a circular shaft hole corresponding to the cylindrical connecting column, the crank structure cylindrical connecting column is vertically arranged on the side surface of the inner gear ring of the rear -stage planetary gear with small tooth difference in the adjacent differential planetary gear with small tooth difference, and the crank structure cylindrical connecting column is inserted into the circular shaft hole of the outer cycloidal gear on the front -stage planetary gear with small tooth difference in the adjacent differential planetary gear with small tooth difference, the crank structure cylindrical connecting column is eccentrically arranged with the circular shaft hole of the outer cycloidal gear, the distance between the axis of the crank structure cylindrical connecting column and the axis of the circular shaft hole is a, the distance between the center of the outer cycloidal gear of the differential planetary gear with small tooth difference and the center of the differential planetary gear with small tooth difference is equal to b, a and b, the second crank structure cylindrical fixed on the end of the crank structure, the end of the second crank structure cylindrical connecting column is inserted into the circular shaft hole of the cylindrical connecting column, and the cylindrical connecting column of the cylindrical crank structure with small tooth difference and the cylindrical connecting column of.
- 3. The planetary gear transmission with small teeth difference as claimed in claim 1, wherein the clutch and the second clutch are both multi-plate hydraulic friction clutches.
- 4. The planetary gear transmission with small teeth difference as claimed in claim 1, wherein the brake is a pneumatic brake.
- 5. The speed variator based on planetary gear with small teeth difference as claimed in claim 1, wherein the casing includes a cylindrical cylinder with left and right ends opened, and the left and right ends of the cylindrical cylinder are covered with "umbrella cover" shaped end covers.
- 6. The type speed variator based on planetary gear with less teeth difference as claimed in claim 5, wherein the "umbrella cover" shaped end cover is connected to the cylindrical barrel by bolts.
- 7. The speed variator based on planetary gear with small teeth difference as claimed in claim 1, wherein the differential planetary gear with small teeth difference is three-stage, and each stage of the differential planetary gear with small teeth difference has the same structure.
- 8. The speed variator based on small tooth difference planetary gear set as claimed in claim 7, wherein the outer cycloidal gear of stage differential small tooth difference planetary gear set is eccentric downward with the outer cycloidal gear of the third stage differential small tooth difference planetary gear set, and the outer cycloidal gear of the second stage differential small tooth difference planetary gear set is eccentric upward.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810724518.8A CN108488335B (en) | 2018-07-04 | 2018-07-04 | speed variator based on small tooth difference planetary gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810724518.8A CN108488335B (en) | 2018-07-04 | 2018-07-04 | speed variator based on small tooth difference planetary gear |
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| Publication Number | Publication Date |
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| CN108488335A CN108488335A (en) | 2018-09-04 |
| CN108488335B true CN108488335B (en) | 2020-01-31 |
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| CN201810724518.8A Expired - Fee Related CN108488335B (en) | 2018-07-04 | 2018-07-04 | speed variator based on small tooth difference planetary gear |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109780149A (en) * | 2019-03-13 | 2019-05-21 | 吉林大学 | A kind of speed change gear based on small teeth number difference planet gear |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2167236Y (en) * | 1993-05-24 | 1994-06-01 | 徐至辉 | Planetary transmission withless leeth difference of dynamic shifting type |
| CN1090024A (en) * | 1993-01-19 | 1994-07-27 | 徐至辉 | Epicyclic variable-speed gear with less difference of number of teeth |
| JP2005016695A (en) * | 2003-06-30 | 2005-01-20 | Hirokazu Tanaka | Reduction gear |
| CN201348024Y (en) * | 2008-12-05 | 2009-11-18 | 天津市正平机械新技术有限公司 | Compound small teeth difference reducing gear |
| CN101881322A (en) * | 2009-05-06 | 2010-11-10 | 徐至辉 | Series-connection type small tooth number difference speed-change mechanism |
| CN105276097A (en) * | 2015-11-25 | 2016-01-27 | 重庆大学 | Double-level differential movement type few-tooth-difference planetary gear transmission mechanism |
-
2018
- 2018-07-04 CN CN201810724518.8A patent/CN108488335B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1090024A (en) * | 1993-01-19 | 1994-07-27 | 徐至辉 | Epicyclic variable-speed gear with less difference of number of teeth |
| CN2167236Y (en) * | 1993-05-24 | 1994-06-01 | 徐至辉 | Planetary transmission withless leeth difference of dynamic shifting type |
| JP2005016695A (en) * | 2003-06-30 | 2005-01-20 | Hirokazu Tanaka | Reduction gear |
| CN201348024Y (en) * | 2008-12-05 | 2009-11-18 | 天津市正平机械新技术有限公司 | Compound small teeth difference reducing gear |
| CN101881322A (en) * | 2009-05-06 | 2010-11-10 | 徐至辉 | Series-connection type small tooth number difference speed-change mechanism |
| CN105276097A (en) * | 2015-11-25 | 2016-01-27 | 重庆大学 | Double-level differential movement type few-tooth-difference planetary gear transmission mechanism |
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