CN105605192A - Optimization method of two-stage straight tooth planet gear - Google Patents
Optimization method of two-stage straight tooth planet gear Download PDFInfo
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- CN105605192A CN105605192A CN201510304099.9A CN201510304099A CN105605192A CN 105605192 A CN105605192 A CN 105605192A CN 201510304099 A CN201510304099 A CN 201510304099A CN 105605192 A CN105605192 A CN 105605192A
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- gear
- optimization method
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- stage straight
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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
- F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
- F16H55/02—Toothed members; Worms
- F16H55/17—Toothed wheels
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Abstract
The invention provides an optimization method of a two-stage straight tooth planet gear, comprising: a, building a static transmission error model; b, acquiring a gear modification load value of a straight tooth planetary wheel transmission case; c, according to the static transmission error model, acquiring a best gear modification quantity. According to the optimization method of the two-stage straight tooth planetary wheel, under the premises of not increasing gear processing precision and saving materials as far as possible, vibration and noise of planetary transmission are effectively reduced, a partial load phenomenon of planetary gear engagement is greatly reduced, further the transmission smoothness of the gear is improved, the carrying capacity of the gear is enhanced, the service life of the gear is prolonged, the cost is reduced, and noise damage to the physical and psychological health of a human body is also reduced.
Description
Technical field
The present invention relates to mechanical field, relate in particular to a kind of optimization method of two-stage straight-tooth planetary gear.
Background technology
Epicyclic gearbox is the mechanism that multiple planetary gears rotate around a sun gear, is also by transmission speed ratioReduce, simultaneously again by the mechanism of the proportional increase of motor torsion. Compare similar full depth tooth physics case, its toolHave transmit steadily, there are large gearratio, particularly life-span in the large and small space of bearing capacity, and volume is small and exquisite,Appearance looks elegant.
Epicyclic gearbox is the vitals of extensive use in machine driving, when the engagement of a pair of gear, due to notCan avoid existing tooth pitch, profile of tooth equal error, in operation process, meeting produces mesh impact and occurs and toothWheel meshing frequency corresponding noise, between the flank of tooth because frictional noise also occurs relative sliding. Due to gearBe the fundamental parts in gearbox drive, reduce grating of gears very necessary to control gear case noise. Generally, the reason that gear train noise occurs mainly contains the following aspects:
1. design of gears aspect. It is improper that parameter is selected, and registration is too small, and profile modification is improper or there is no a correction of the flank shape,Gear box structure is unreasonable etc. Gear Processing aspect base pitch error and profile error are excessive, and backlash is excessive,Surface roughness is excessive etc.
2. gear train and gear-box aspect. Assembling is eccentric, and contact precision is low, and the depth of parallelism of axle is poor, axle, axleThe insufficient rigidity of holding, supporting, the not high and gap of the rotating accuracy of bearing is improper etc.
3. other aspect input torques. The fluctuation of load torque, torsional oscillation, motor and other transmission of axle systemSecondary balance etc.
The calculating side that the mentality of designing of tradition epicyclic gearbox generally combines with experience according to the theory of simplifyingMethod, gear teeth face is designed to the involute flank of standard, can make so in theory gear nibble preferablyClose, but due to processing and the existence of rigging error, in addition under load due to gear body and gearSupport component makes generation strain field of conjugate action deviation theory involute and also can make meshing zone of gears territory along toothCross direction produces certain unbalance loading phenomenon, makes so on the one hand gear-box produce larger vibration and noise; SeparatelyMake flank of tooth unbalance stress and the fatigue rupture of accelerating gear on the one hand. In order to change above deficiency, conventional methodIt is the support stiffness that improves the accuracy of manufacture grade of whole gear-box and increase gear. But increase so on the one handAdd manufacture difficulty and processing cost, reduced the operating efficiency of gear-box simultaneously.
Summary of the invention
In view of this, the invention provides a kind of optimization method of two-stage straight-tooth planetary gear, to address the above problem.
The optimization method of two-stage straight-tooth planetary gear provided by the invention, comprises
A. set up quiet transmission error model,
B. obtain the load value of the gear modification of straight-tooth planet gear transmission box,
C. obtain best gear modification amount according to quiet transmission error model.
Further, described quiet transmission error model is:
TE＝θ2rb2-θ1rb1
Wherein, TE is quiet transmission error, θ1For driving gear actual rotational angle, θ2For driven gear actual rotational angle,rb1For driving gear base radius, rb2For driven gear base radius.
Further, described quiet transmission error for being produced by gear shifting quadrant texturing and gear error under static conditionsKinematic error.
Further, load value described in step b is the rated load of two-stage straight-tooth planet gear transmission box.
Further, described in step c, gear modification amount comprises profile modification and axial modification.
Further, the minimum of a value of choosing quiet transmission error functional value is optimum gear speed profiling quantity.
Beneficial effect of the present invention: the optimization method of two-stage straight-tooth planetary gear provided by the invention, can be notImprove Gear Processing precision and save under the prerequisite of material as far as possible, vibration and the noise of Gear Planet Transmission have obtainedThe reduction of effect, has reduced the unbalance loading phenomenon of planetary gear engagement greatly, and then it is flat to have improved the transmission of gearStability, has improved the bearing capacity of gear, has extended the service life of gear, has not only saved cost, anotherAlso reduce on the one hand the able-bodied injury of noise on human body.
Brief description of the drawings
Below in conjunction with drawings and Examples, the invention will be further described:
Fig. 1 is principle schematic of the present invention.
Fig. 2 is profile modification parameter schematic diagram of the present invention.
Fig. 3 is driving error peak-to-peak value schematic diagram of the present invention.
Fig. 4 is axial modification parameter schematic diagram of the present invention.
The normal load peak value schematic diagram of unit length when Fig. 5 is flank of tooth contact of the present invention.
Detailed description of the invention
Below in conjunction with drawings and Examples, the invention will be further described: Fig. 1 is principle signal of the present inventionFigure, Fig. 2 is profile modification parameter schematic diagram of the present invention, Fig. 3 is that driving error peak-to-peak value of the present invention showsIntention, Fig. 4 is axial modification parameter schematic diagram of the present invention, Fig. 5 is that the flank of tooth of the present invention contacts time unitThe normal load peak value schematic diagram of length.
As shown in Fig. 1,2,3,4,5, the optimization method of two-stage straight-tooth planetary gear of the present invention, comprises
A. set up quiet transmission error model,
B. obtain the load value of the gear modification of straight-tooth planet gear transmission box,
C. obtain best gear modification amount according to quiet transmission error model.
In the present embodiment, as shown in Figure 2, the Tooth Modification of Involute Spur of two flank of tooth of planetary gear all comprises:Tooth top correction of the flank shape starting point (right contact-making surface is point 3, and left contact-making surface is point 1) and tooth root correction of the flank shape starting point (right contactFace for point 4, left contact-making surface for point 2) and tooth top profiling quantity (right contact-making surface is Δ3, left contact-making surface is Δ1) with(right contact-making surface is Δ to tooth root profiling quantity4, left contact-making surface is Δ2). During due to two gear engagements, it is at tooth topBasic identical with the engagement situation of tooth root, thus the principle that adopts tooth top profiling quantity to equate with tooth root profiling quantity,It is Δ1＝Δ2And Δ3＝Δ4, taking profiling quantity as design variable, the peak value of driving error is functional value, by repeatedlyComputing obtains a series of values. For the excitation of displacement type, by the distortion of the gear teeth under load and gear mistakePoor both combine, and represent to become quiet transmission error, under static conditions by gear shifting quadrant texturing and gear errorThe kinematic error producing, when being defined as driving gear and rotating a certain angle, driven gear physical location (is revolvedGyration) and theoretical position between deviation,
Formula table along path of contact direction is shown
TE＝θ2rb2-θ1rb1Formula (2)
Wherein, TE is quiet transmission error, θ1、θ2Be respectively active and passive gear actual rotational angle, i is gearGearratio, rb1、rb2Be respectively active and passive gear base radius.
In the present embodiment, as shown in a, b in Fig. 3, find the minimum corresponding profiling quantity of functional value to beBest profile modification amount. Second level Gear Planet Transmission profile modification also adopts identical with first order Gear Planet TransmissionMethod is definite, and the function of its driving error is as shown in c, d in Fig. 3.
In the present embodiment, adopt the method for cydariform correction of the flank shape, respectively two different contact-making surfaces are carried out to cydariformCorrection of the flank shape. As shown in Figure 4, two different flank of tooth cydariform modification curves comprise: cydariform center and the cydariform amount (right sideContact-making surface is h, and left contact-making surface is g). Cydariform center is chosen in the centre of the facewidth. Determining of cydariform amount,Adopt all taking cydariform amount as design variable, the normal load peak value of flank of tooth unit length is functional value, by manyInferior computing obtains a series of values, as shown in a, b in Fig. 5, finds some values that functional value is less, more comprehensiveConsider that load should be distributed in the centre position of the flank of tooth as far as possible, finds best cydariform amount. As c, d in Fig. 5Shown in second level Gear Planet Transmission axial modification also adopt the method identical with first order Gear Planet Transmission to determine, it is singleThe load peaks function of bit length.
Finally explanation, above embodiment is only unrestricted in order to technical scheme of the present invention to be described, althoughWith reference to preferred embodiment, the present invention is had been described in detail, those of ordinary skill in the art should be appreciated thatCan modify or be equal to replacement technical scheme of the present invention, and not depart from technical solution of the present inventionAim and scope, it all should be encompassed in the middle of claim scope of the present invention.
Claims (6)
1. an optimization method for two-stage straight-tooth planetary gear, is characterized in that: comprise
A. set up quiet transmission error model,
B. obtain the load value of the gear modification of straight-tooth planet gear transmission box,
C. obtain best gear modification amount according to quiet transmission error model.
2. the optimization method of two-stage straight-tooth planetary gear according to claim 1, is characterized in that: described inQuiet transmission error model is:
TE＝θ2rb2-θ1rb1
Wherein, TE is quiet transmission error, θ1For driving gear actual rotational angle, θ2For driven gear actual rotational angle,rb1For driving gear base radius, rb2For driven gear base radius.
3. the optimization method of two-stage straight-tooth planetary gear according to claim 2, is characterized in that: described inThe kinematic error of quiet transmission error for being produced by gear shifting quadrant texturing and gear error under static conditions.
4. the optimization method of two-stage straight-tooth planetary gear according to claim 1, is characterized in that: stepLoad value described in b is the rated load of two-stage straight-tooth planet gear transmission box.
5. the optimization method of two-stage straight-tooth planetary gear according to claim 1, is characterized in that: stepThe amount of gear modification described in c comprises profile modification and axial modification.
6. the optimization method of two-stage straight-tooth planetary gear according to claim 5, is characterized in that: chooseThe minimum of a value of quiet transmission error functional value is optimum gear speed profiling quantity.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510304099.9A CN105605192A (en) | 2015-06-04 | 2015-06-04 | Optimization method of two-stage straight tooth planet gear |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510304099.9A CN105605192A (en) | 2015-06-04 | 2015-06-04 | Optimization method of two-stage straight tooth planet gear |
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| CN105605192A true CN105605192A (en) | 2016-05-25 |
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| CN201510304099.9A Pending CN105605192A (en) | 2015-06-04 | 2015-06-04 | Optimization method of two-stage straight tooth planet gear |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106763642A (en) * | 2017-02-22 | 2017-05-31 | 北京新能源汽车股份有限公司 | Noise reduction method for electric automobile speed reducer and electric automobile speed reducer |
| CN108519224A (en) * | 2018-03-16 | 2018-09-11 | 华南理工大学 | A method of verification two-stage fixed axis gear transmission system vibration coupling feature |
| CN109915566A (en) * | 2019-03-29 | 2019-06-21 | 重庆大学 | A kind of lifting gear box of self-lifting ocean |
Citations (4)
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| US5605518A (en) * | 1993-03-26 | 1997-02-25 | Hitachi, Ltd. | Planetary gear device |
| JPH10506172A (en) * | 1994-08-01 | 1998-06-16 | アキシコン ギアー カンパニー | Phase correction of gear teeth by crowning |
| CN1936749A (en) * | 2006-10-18 | 2007-03-28 | 华中科技大学 | Evolent straight-gear conic-gear direct-finishing method |
| 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 |
-
2015
- 2015-06-04 CN CN201510304099.9A patent/CN105605192A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5605518A (en) * | 1993-03-26 | 1997-02-25 | Hitachi, Ltd. | Planetary gear device |
| JPH10506172A (en) * | 1994-08-01 | 1998-06-16 | アキシコン ギアー カンパニー | Phase correction of gear teeth by crowning |
| CN1936749A (en) * | 2006-10-18 | 2007-03-28 | 华中科技大学 | Evolent straight-gear conic-gear direct-finishing method |
| 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 |
Non-Patent Citations (1)
| Title |
|---|
| 冯锦平、马文礼: "直齿轮齿距误差与齿高修形综合设计", 《机械设计与制造》 * |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106763642A (en) * | 2017-02-22 | 2017-05-31 | 北京新能源汽车股份有限公司 | Noise reduction method for electric automobile speed reducer and electric automobile speed reducer |
| CN106763642B (en) * | 2017-02-22 | 2020-09-04 | 北京新能源汽车股份有限公司 | Noise reduction method for electric automobile speed reducer and electric automobile speed reducer |
| CN108519224A (en) * | 2018-03-16 | 2018-09-11 | 华南理工大学 | A method of verification two-stage fixed axis gear transmission system vibration coupling feature |
| CN109915566A (en) * | 2019-03-29 | 2019-06-21 | 重庆大学 | A kind of lifting gear box of self-lifting ocean |
| CN109915566B (en) * | 2019-03-29 | 2022-03-08 | 重庆大学 | Self-elevating ocean platform lifting gear box |
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