CN202812052U - Helical gear planet transmission system with tooth surface modification - Google Patents
Helical gear planet transmission system with tooth surface modification Download PDFInfo
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- CN202812052U CN202812052U CN 201220013991 CN201220013991U CN202812052U CN 202812052 U CN202812052 U CN 202812052U CN 201220013991 CN201220013991 CN 201220013991 CN 201220013991 U CN201220013991 U CN 201220013991U CN 202812052 U CN202812052 U CN 202812052U
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- Prior art keywords
- gear
- helical gear
- outer oblique
- transmission system
- tooth surface
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Abstract
A helical gear planet transmission system with tooth surface modification includes two engaged transmission gears of an inner helical gear pair and an outer helical gear pair, wherein an outer helical gear in the planet transmission system employs non-involute profile after the tooth surface modification, while an inner helical gear still employs the standard involute profile. The helical gear planet transmission system with the tooth surface modification includes the inner and the outer helical gear pairs which are transmitted through a parallel shaft. As the outer helical gear pair is the gear modified by a plunge grinding method, a " local conjugate " phenomenon containing a certain transmission error exits during the engagement of the gear pair, after application of the load, the vibration and noise of a small planetary gear transmission can be effectively reduced, thereby lifting the integral performance of high speed heavy duty planetary gear speed reducer (increaser) in our country.
Description
Technical field
The utility model belongs to mechanical engineering field, and particularly a kind of helical gear Gear Planet Transmission that contains axial modification of using in machine driven system subtracts (increasing) fast device.
Background technique
Planetary gear speed reducer has that volume is little, bearing capacity is large, gear range is large, the transmission efficiency advantages of higher, is used widely in aviation, automobile etc. field.According to the Involutes Gears Transmission condition, the gear in the planetary transmission system always keeps " an oblique homocline, always all straight ".For 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 manufacture 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 also imperfect in the actual use of this in theory " total conjugated " engagement system.Exist in the situation of certain alignment error, two flank of tooth change a contact into by the Molded Line contact, and the contact path favours the base cylinder bus, and its how much driving errors are discontinuous straightway, produce easily vibration and noise during engagement, and EDGE CONTACT occurs easily.A large amount of practices and theory analysis show, 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 and distribute, 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.
The model utility content
The utility model is a kind of helical gear planetary transmission system that adopts axial modification that proposes for the deficiency of existing planetary driving device, 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 utility model is that the technological scheme that the deficiency that solves the problems of the technologies described above adopts is: the helical gear planetary transmission system that adopts axial modification, internal helical gear and outer oblique gear are cylindrical gears, 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, sun gear is 1, planet wheel is 1～6, form planetary gear train with internal helical gear, the flank of tooth of described 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, the flank of tooth vector equation after the described planet wheel correction of the flank shape is
The utility model beneficial effect is:
1, the utility model proposes the driving error curve is preset to high-order driving error curve, improve transmission performance by axial modification.
2, the utility model is set up the dynamic model of Helical Gears with Modification 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 impact of the dynamic characteristic of helical gear pair by Parameter Sensitivity Analysis.
3, the utility model put into practice can Effective Raise helical gear planetary driving device bearing capacity, reduce vibration and noise.
Description of drawings
Fig. 1 is the utility model structural representation;
Fig. 2 is that the utility model is interrupted linear engagement circulation transmission curve schematic representation;
Fig. 3 is the utility model second-degree parabola correction of the flank shape driving error curve;
Fig. 4 is that circulation transmission curve schematic representation is meshed in the correction of the flank shape of the utility model second-degree parabola continuously;
Fig. 5 is the utility model high-order driving error function;
Fig. 6 is the end section profile of the utility model Helical Gears with Modification;
Fig. 7 is the utility model correction of the flank shape outer oblique gear form grinding system of coordinates;
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, 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, the teeth directional direction of outer oblique gear 5 and the axial direction of outer oblique gear 5 are in a certain angle, described outer oblique gear 5 comprises sun gear 2 and planet wheel 4, 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 described 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 utility model proposes the driving error curve is preset to high-order driving error curve, improve transmission performance by axial modification.
The utility model is set up the dynamic model of Helical Gears with Modification 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 impact of the dynamic characteristic of helical gear pair by Parameter Sensitivity Analysis.
The utility model put into practice can Effective Raise helical gear planetary driving device bearing capacity, reduce vibration and noise.
The utility model adopts the axial modification method based on the high-order driving error.High-order driving error function expression is:
（1）
Preset key point on the high-order driving error curve and the slope value of transition point, can obtain polynomial coefficient by solving equations
x 0 , x 1 , x 2 , x 3 , x 4 ,Finish finding the solution of high-order driving error function.
In accompanying drawing 6,
,
Be the driving wheel number of teeth.
Take a driving wheel number of teeth as 50, the driven wheel number of teeth is 100, and modulus is that 5 gear is example, then
, establish:
Order:
,
,
,
Then:
That is:
Substitution formula (1):
Determining and to be determined by two kinds of approach about correction of the flank shape outer oblique gear profile of tooth.A kind of is to preset first correction of the flank shape outer oblique gear profile of tooth, by flank profil, axial modification, draws the tooth surface equation of correction of the flank shape outer oblique gear; Then carry out LOADED TOOTH CONTACT ANALYSIS with the standard internal helical gear, 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 represents 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:
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.
Adopt the method for nonlinear contact mechanics to the drive characteristic analysis under the various alignment errors of gear and the carrying condition, whether the check EDGE CONTACT exists, and further optimizes high-order driving error function.Set up the dynamic model of Helical Gears with Modification 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 impact of the dynamic characteristic of helical gear pair by Parameter Sensitivity Analysis.To reduce vibration, inhibition noise as target, carry out helical gear pair driving error comparative trial, thereby further optimize the design parameter of correction of the flank shape backgear pair.
The utility model both can be applied to the general driving of parallel axes, also can be applied to Gear Planet Transmission.Any those skilled in the art all belong to protection category of the present utility model in any simple modification, equivalent variations and the modification above-mentioned transmission system done based on technical solutions of the utility model.
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, the axial direction of the teeth directional direction of outer oblique gear (5) and outer oblique gear (5) is in a certain angle, described outer oblique gear (5) comprises sun gear (2) and planet wheel (4), sun gear (2) is 1, planet wheel (4) is 1～6, form planetary gear train with internal helical gear (1), it is characterized in that: the flank of tooth of described 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 is
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220013991 CN202812052U (en) | 2012-01-13 | 2012-01-13 | Helical gear planet transmission system with tooth surface modification |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220013991 CN202812052U (en) | 2012-01-13 | 2012-01-13 | Helical gear planet transmission system with tooth surface modification |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202812052U true CN202812052U (en) | 2013-03-20 |
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ID=47870925
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201220013991 Expired - Fee Related CN202812052U (en) | 2012-01-13 | 2012-01-13 | Helical gear planet transmission system with tooth surface modification |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202812052U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102537220A (en) * | 2012-01-13 | 2012-07-04 | 河南科技大学 | Planetary transmission system with bevel gears subjected to axial modification |
| CN103527744A (en) * | 2013-10-23 | 2014-01-22 | 中国北方发动机研究所(天津) | Method for compensating for interference gear tooth profile deformation |
| CN111637200A (en) * | 2020-06-12 | 2020-09-08 | 苏州大学 | Helical gear planetary transmission mechanism |
-
2012
- 2012-01-13 CN CN 201220013991 patent/CN202812052U/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102537220A (en) * | 2012-01-13 | 2012-07-04 | 河南科技大学 | Planetary transmission system with bevel gears subjected to axial modification |
| CN103527744A (en) * | 2013-10-23 | 2014-01-22 | 中国北方发动机研究所(天津) | Method for compensating for interference gear tooth profile deformation |
| CN111637200A (en) * | 2020-06-12 | 2020-09-08 | 苏州大学 | Helical gear planetary transmission mechanism |
| WO2021248761A1 (en) * | 2020-06-12 | 2021-12-16 | 苏州大学 | Bevel gear planetary transmission mechanism |
| CN111637200B (en) * | 2020-06-12 | 2022-06-14 | 苏州大学 | Helical gear planetary transmission mechanism |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20130320 Termination date: 20150113 |
|
| EXPY | Termination of patent right or utility model |