CN102537220A - Planetary transmission system with bevel gears subjected to axial modification - Google Patents
Planetary transmission system with bevel gears subjected to axial modification Download PDFInfo
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- CN102537220A CN102537220A CN2012100096293A CN201210009629A CN102537220A CN 102537220 A CN102537220 A CN 102537220A CN 2012100096293 A CN2012100096293 A CN 2012100096293A CN 201210009629 A CN201210009629 A CN 201210009629A CN 102537220 A CN102537220 A CN 102537220A
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Abstract
A planetary transmission system with bevel gears subjected to axial modification comprises an internal bevel gear set and an external bevel gear set which are in meshing transmission. External bevel gears in the planetary transmission system have non-involute tooth profile subjected to axial modification, and internal bevel gears have standard involute tooth profile. The internal bevel set and the external bevel set realize parallel axis transmission. As the external bevel gears are modified by the form grinding process, 'local conjugate' of a certain amount of transmission errors is caused when in meshing of the gear set, vibration and noise of planetary gears in transmission can be reduced effectively after load is applied, and accordingly the comprehensive performance of domestic high-speed heavy-load planetary gear reducers (increasers) can be improved.
Description
Technical field
The invention belongs to mechanical engineering field, particularly a kind of helical gear Gear Planet Transmission of in machine driven system, using that contains axial modification subtracts (increasing) fast device.
Background technique
Planetary gear speed reducer has that volume is little, bearing capacity is big, gear range is big, the transmission efficiency advantages of higher, is used widely in aviation, automobile or the like field.According to the Involutes Gears Transmission condition, the gear in the planetary transmission system always keeps " an oblique homocline, all straight always ".From the reason of manufacture view, planetary type gear transmission unit adopts straight-tooth more both at home and abroad.Recently; More external companies have begun the design and the manufacturing of helical teeth planetary driving device; As the U.S. Ai Lixun automatic transmission that is described as " king of heavy automatic transmission " all adopts the helical teeth plane table thermoconductivity meter, and volume, vibration, noise etc. are all reduced to some extent.
But it is also imperfect in the actual use of this " total conjugated " in theory engagement system.Exist under the situation of certain alignment error; Two flank of tooth are by Molded Line contact changing into a contact, and the contact path favours the base cylinder bus, and its how much driving errors are discontinuous straightway; Be easy to generate vibration and noise during engagement, and EDGE CONTACT takes place easily.A large amount of practices show with theory analysis, and involute flank is carried out " local conjugation " gear pair after certain correction of the flank shape, can reduce gear engaging-in, nibble out impact, improve load distribution, reduce and vibrate and noise.To introduce in the helical teeth Gear Planet Transmission based on the axial modification technology of high-order driving error, be intended to further improve the dynamic characteristic of Gear Planet Transmission.
Summary of the invention
The present invention be directed to the deficiency that has planetary driving device now and a kind of helical gear planetary transmission system that adopts axial modification that proposes, be intended to further improve the load distribution of Gear Planet Transmission, reduce vibration and noise, improve the dynamic characteristic of Gear Planet Transmission.
The present invention is that the technological scheme that the deficiency that solves the problems of the technologies described above adopts is: adopt the helical gear planetary transmission system of axial modification, internal helical gear and outer oblique gear are cylindrical gears, and the axis of internal helical gear and outer oblique gear is parallel to each other; The teeth directional direction of outer oblique gear and the axial direction of outer oblique gear are in a certain angle; Described outer oblique gear comprises sun gear and planet wheel, and sun gear is 1, and planet wheel is 1～6; Form planetary gear train with internal helical gear; The flank of tooth of said outer oblique gear carries out correction of the flank shape, the not correction of the flank shape of internal helical gear that is meshed with outer oblique gear, and the flank of tooth vector equation after the described planet wheel correction of the flank shape does
Beneficial effect of the present invention is:
1, the present invention proposes the driving error curve is preset to high-order driving error curve, improves transmission performance through axial modification.
2, the present invention sets up the dynamic model of correction of the flank shape helical gear transmission; Calculate its mesh stiffness, damping constant, natural frequency and the vibration shape; Research gear parameter and profiling quantity carry out the dynamic optimization design of gear train to the influence of the dynamic characteristic of helical gear pair through Parameter Sensitivity Analysis.
3, the present invention puts into practice and can effectively improve the bearing capacity of helical gear planetary driving device, reduces vibration and noise.
Description of drawings
Fig. 1 is a structural representation of the present invention;
Fig. 2 is that the present invention is interrupted linear engagement circulation transmission curve schematic representation;
Fig. 3 is a second-degree parabola correction of the flank shape driving error curve of the present invention;
Fig. 4 is that circulation transmission curve schematic representation is meshed in second-degree parabola correction of the flank shape of the present invention continuously;
Fig. 5 is a high-order driving error function of the present invention;
Fig. 6 is the helical gear end section profile of correction of the flank shape of the present invention;
Fig. 7 is a correction of the flank shape outer oblique gear form grinding system of coordinates of the present invention;
Among the figure: 1, internal helical gear, 2, sun gear, 3, planet carrier, 4, planet wheel, 5, outer oblique gear.
Embodiment
As shown in the figure, the helical gear planetary transmission system of employing axial modification, internal helical gear 1 is cylindrical gears with outer oblique gear 5; The axis of internal helical gear 1 and outer oblique gear 5 is parallel to each other; The teeth directional direction of outer oblique gear 5 and the axial direction of outer oblique gear 5 are in a certain angle, and described outer oblique gear 5 comprises sun gear 2 and planet wheel 4, and sun gear 2 is 1; Planet wheel 4 is 1～6; Form planetary gear train with internal helical gear 1, the flank of tooth of said outer oblique gear 5 carries out correction of the flank shape, the internal helical gear 1 not correction of the flank shape that is meshed with outer oblique gear 5.
The present invention proposes the driving error curve is preset to high-order driving error curve, improves transmission performance through axial modification.
The present invention sets up the dynamic model of correction of the flank shape helical gear transmission; Calculate its mesh stiffness, damping constant, natural frequency and the vibration shape; Research gear parameter and profiling quantity carry out the dynamic optimization design of gear train to the influence of the dynamic characteristic of helical gear pair through Parameter Sensitivity Analysis.
The present invention puts into practice and can effectively improve the bearing capacity of helical gear planetary driving device, reduces vibration and noise.
The present invention adopts the axial modification method based on the high-order driving error.High-order driving error function expression is:
Preset key point and the slope value of transition point on the high-order driving error curve, group can be obtained polynomial coefficient through solving an equation
x 0 , x 1 , x 2 , x 3 , x 4 ,Accomplish finding the solution of high-order driving error function.
In accompanying drawing 5;
,
is the driving wheel number of teeth.
With a driving wheel number of teeth is 50; The driven wheel number of teeth is 100; Modulus is that 5 gear is an example; Then
, establish:
Order:
;
;
Then:
That is:
Substitution formula (1):
Can confirm by two kinds of approach about correction of the flank shape outer oblique gear Profile Determination.A kind of is earlier preset correction of the flank shape outer oblique gear profile of tooth, through flank profil, axial modification, draws the tooth surface equation of correction of the flank shape outer oblique gear; Carry out LOADED TOOTH CONTACT ANALYSIS with the standard internal helical gear then, further optimize the correction of the flank shape coefficient.Another kind is by the profile of tooth envelope of the standard internal helical gear helical gear profile of tooth of going out.This method just is difficult to write out the tooth surface equation of concrete correction of the flank shape outer oblique gear, and it is along with the variation of operating mode changes, but can ask.
If accompanying drawing 6 is depicted as the end section profile of correction of the flank shape outer oblique gear, dotted line representation theory involute wherein, solid line is represented the correction of the flank shape involute.Accompanying drawing 7 is depicted as the grinding motion system of coordinates of form grinding correction of the flank shape outer oblique gear.S
f , S
2, S
tRepresentative is based upon lathe coordinate system, workpiece coordinate system, emery wheel system of coordinates respectively.By system of coordinates S
tTo S
2Transformation matrix of coordinates be:
Teeth groove cross section vector equation in the middle of the width of the workpiece is:
Then the flank of tooth vector equation of gear is:
（4）
That is:
Wherein, a
pBe coefficient, can choose;
It is Base radius;
It is the angle of spread;
It is profiling quantity; σ
02It is the basic circle teeth groove half-angle of outer oblique gear;
It is the helix coefficient.
The method that adopts the nonlinear contact mechanics is to the drive characteristic analysis under various alignment errors of gear and the carrying condition, and whether the check EDGE CONTACT exists, and further optimizes high-order driving error function.Set up the dynamic model of correction of the flank shape helical gear pair; Calculate its mesh stiffness, damping constant, natural frequency and the vibration shape; Research gear parameter and profiling quantity carry out the dynamic optimization design of gear train to the influence of the dynamic characteristic of helical gear pair through Parameter Sensitivity Analysis.With reduce vibration, inhibitions noise is target, carries out helical gear pair driving error comparative trial, thereby further optimize the design parameter of correction of the flank shape backgear pair.
The present invention both can be applied to the general driving of parallel axes, also can be applied to Gear Planet Transmission.Any professional and technical personnel of being familiar with all belongs to protection category of the present invention in any simple modification, equivalent variations and the modification above-mentioned transmission system done based on technological scheme of the present invention.
Claims (1)
1. adopt the helical gear planetary transmission system of axial modification; Internal helical gear (1) and outer oblique gear (5) are cylindrical gears; The axis of internal helical gear (1) and outer oblique gear (5) is parallel to each other, and the axial direction of the teeth directional direction of outer oblique gear (5) and outer oblique gear (5) is in a certain angle, and described outer oblique gear (5) comprises sun gear (2) and planet wheel (4); Sun gear (2) is 1; Planet wheel (4) is 1～6, forms planetary gear train with internal helical gear (1), and it is characterized in that: the flank of tooth of said outer oblique gear (5) carries out correction of the flank shape; The not correction of the flank shape of internal helical gear (1) that is meshed with outer oblique gear (5), the flank of tooth vector equation after described planet wheel (4) correction of the flank shape does
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012100096293A CN102537220A (en) | 2012-01-13 | 2012-01-13 | Planetary transmission system with bevel gears subjected to axial modification |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2012100096293A CN102537220A (en) | 2012-01-13 | 2012-01-13 | Planetary transmission system with bevel gears subjected to axial modification |
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| CN102537220A true CN102537220A (en) | 2012-07-04 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2012100096293A Pending CN102537220A (en) | 2012-01-13 | 2012-01-13 | Planetary transmission system with bevel gears subjected to axial modification |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103577713A (en) * | 2013-11-21 | 2014-02-12 | 上海理工大学 | Calculation method for diagonal modification amount of bevel gear pair |
| CN107081678A (en) * | 2017-07-04 | 2017-08-22 | 河南科技大学 | A kind of formation grinding of cycloid wheel grinding wheel dressing method |
| CN112487586A (en) * | 2020-12-18 | 2021-03-12 | 北京航空航天大学 | Design method for high-speed heavy-load GTF double-helix gear large-spread-angle tooth profile |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5802921A (en) * | 1996-08-13 | 1998-09-08 | Rouverol; William S. | Maximum power density gearing |
| JP2008101700A (en) * | 2006-10-19 | 2008-05-01 | Enplas Corp | Pair of resin double helical gears |
| CN102218572A (en) * | 2011-05-31 | 2011-10-19 | 中国航空动力机械研究所 | Shaping method and manufacturing method for involute straight tooth planetary transmission gear |
| CN102314534A (en) * | 2011-06-03 | 2012-01-11 | 东北大学 | Gear profile modification method based on vibration reliability and genetic algorithm |
| CN202812052U (en) * | 2012-01-13 | 2013-03-20 | 河南科技大学 | Helical gear planet transmission system with tooth surface modification |
-
2012
- 2012-01-13 CN CN2012100096293A patent/CN102537220A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5802921A (en) * | 1996-08-13 | 1998-09-08 | Rouverol; William S. | Maximum power density gearing |
| JP2008101700A (en) * | 2006-10-19 | 2008-05-01 | Enplas Corp | Pair of resin double helical gears |
| CN102218572A (en) * | 2011-05-31 | 2011-10-19 | 中国航空动力机械研究所 | Shaping method and manufacturing method for involute straight tooth planetary transmission gear |
| CN102314534A (en) * | 2011-06-03 | 2012-01-11 | 东北大学 | Gear profile modification method based on vibration reliability and genetic algorithm |
| CN202812052U (en) * | 2012-01-13 | 2013-03-20 | 河南科技大学 | Helical gear planet transmission system with tooth surface modification |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103577713A (en) * | 2013-11-21 | 2014-02-12 | 上海理工大学 | Calculation method for diagonal modification amount of bevel gear pair |
| CN103577713B (en) * | 2013-11-21 | 2016-08-17 | 上海理工大学 | A kind of computational methods of diagonal modification amount of bevel gear pair |
| CN107081678A (en) * | 2017-07-04 | 2017-08-22 | 河南科技大学 | A kind of formation grinding of cycloid wheel grinding wheel dressing method |
| CN107081678B (en) * | 2017-07-04 | 2020-01-07 | 河南科技大学 | Method for dressing grinding wheel for forming and grinding cycloid wheel |
| CN112487586A (en) * | 2020-12-18 | 2021-03-12 | 北京航空航天大学 | Design method for high-speed heavy-load GTF double-helix gear large-spread-angle tooth profile |
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Application publication date: 20120704 |