CN110083939A - Pure electric vehicle differential gear correction of the flank shape optimization method - Google Patents
Pure electric vehicle differential gear correction of the flank shape optimization method Download PDFInfo
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- 238000005457 optimization Methods 0.000 title claims abstract description 43
- 238000000034 method Methods 0.000 title claims abstract description 22
- 238000012986 modification Methods 0.000 claims abstract description 121
- 230000004048 modification Effects 0.000 claims abstract description 119
- 238000004088 simulation Methods 0.000 claims description 49
- 238000010862 gear shaping Methods 0.000 claims description 4
- 235000000621 Bidens tripartita Nutrition 0.000 claims description 2
- 240000004082 Bidens tripartita Species 0.000 claims description 2
- 208000006637 fused teeth Diseases 0.000 claims description 2
- 238000007493 shaping process Methods 0.000 claims description 2
- 230000005540 biological transmission Effects 0.000 abstract description 9
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- 238000004519 manufacturing process Methods 0.000 description 3
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- 230000005489 elastic deformation Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
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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
- F16H55/08—Profiling
- F16H55/0886—Profiling with corrections along the width, e.g. flank width crowning for better load distribution
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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
- F16H55/14—Construction providing resilience or vibration-damping
- F16H55/16—Construction providing resilience or vibration-damping relating to teeth only
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
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Abstract
The present invention discloses a kind of pure electric vehicle differential gear correction of the flank shape optimization method, includes the following steps: (10) differential gear three-dimension modeling: according to spur bevel gear parameter, establishing axle shaft gear and planetary gear threedimensional model；(20) single planetary gear profile modification: section is optimized according to profile modification, carries out threedimensional model emulation；(30) single planetary gear axial modification: section is optimized according to planetary gear teeth directional correction of the flank shape, carries out threedimensional model emulation；(40) it full differential gear profile modification: is emulated single planetary gear profile modification optimal value as the complete total optimal value of differential gear profile modification, obtains full differential gear profile modification optimal solution；(50) it full differential gear axial modification: is emulated single planetary gear axial modification optimal value as the complete total optimal value of differential gear axial modification, obtains full differential gear axial modification optimal solution.Gear modification optimization method of the present invention, differential gear transmission stability is good, noise is low, fatigue life is long.
Description
Technical Field
The invention belongs to the technical field of gear modification, and particularly relates to a gear modification optimization method for a differential mechanism of a pure electric vehicle.
Background
The straight bevel gear is used for transmitting power in a differential gear of a vehicle, but the differential gear can generate elastic deformation in the meshing process because of the manufacturing process and errors and the change of a transmission ratio because a pure electric vehicle does not have a transmission, so that the gear is suddenly stressed too much in the actual meshing process to generate larger transmission errors and noises, and the fatigue life of the gear is greatly reduced. The influence caused by the problems can be reduced and the reliability of the gear is improved through gear modification.
The Chinese patent application 'optimization method for modifying involute straight-tooth gear' (application number: 201510564613.2, published: 2015-12-16) discloses an optimization method for modifying involute straight-tooth gear, which comprises the following steps: and optimizing the preliminarily determined equidistant modification range and modification interval twice to determine an interval needing modification optimization of the gear, and modifying the addendum and the tooth profile curve of the driving gear and the driven gear with the same value to obtain the modified gear. The shape modification method lacks more accurate parameter optimization and lacks gear pair linkage matching optimization.
The Chinese invention patent application 'a gear shaping method' (application number: 201710040488.4, published: 2017-05-24) discloses a gear shaping method, which comprises the following steps: performing blank-feeding rough machining according to gear parameters, performing heat treatment, semi-finishing and hobbing, and finally performing modification treatment of the tooth direction and the tooth shape, wherein the modification parameters are set according to an empirical formula of each modification amount. The gear shaping method mainly adopts finish machining after rough manufacturing and shaping according to an empirical formula, and lacks more accurate parameter optimization.
Therefore, the prior art has the problems that: because the pure electric vehicle is not provided with a transmission, the stress of a differential gear is not uniform in the processes of sudden starting, braking and driving of the electric vehicle, the stress condition is very severe, and the braking energy recovery process exists in the pure electric vehicle, so that the gear transmission stability of the differential gear of the pure electric vehicle is not good enough, the noise is large, and the fatigue life is short.
Disclosure of Invention
The invention aims to provide a method for optimizing the shape modification of a differential gear of a pure electric vehicle, which has the advantages of good transmission stability of the differential gear, low noise and long fatigue life.
The technical solution for realizing the purpose of the invention is as follows:
a pure electric vehicle differential gear modification optimization method comprises the following steps:
(10) establishing a three-dimensional model of a differential gear: according to parameters of the straight bevel gear, a mathematical equation of the straight bevel gear is combined, and three-dimensional models of the half axle gear and the planetary gear are established;
(20) single planetary gear profile modification: obtaining a single planetary gear tooth profile modification optimal value through three-dimensional model simulation according to the planetary gear tooth profile modification optimization interval and the tooth profile modification curve formula;
(30) single planetary gear tooth axial modification: according to the planetary gear tooth direction modification optimization interval, obtaining a single planetary gear tooth direction modification optimal value through three-dimensional model simulation;
(40) modification of the gear tooth profile of the full differential: taking the optimal value of the profile modification of the single planetary gear as the total optimal value of the profile modification of the gear of the full differential, equally dividing the optimal value of the profile modification of the single planetary gear into 8 grades, determining 9 groups of parameters of the profile modification of the gear of the differential, carrying out simulation, and taking one group with the optimal simulation result as the optimal solution of the profile modification of the gear of the full differential;
(50) axial modification of the gear of the full differential: and taking the tooth direction modification optimal value of the single planetary gear as the total tooth direction modification optimal value of the full differential gear, equally dividing the tooth direction modification optimal value of the single planetary gear into 8 levels, determining 9 groups of differential gear tooth direction modification parameters, performing simulation, and taking one group with the optimal simulation result as the optimal solution of the tooth direction modification of the full differential gear.
Compared with the prior art, the invention has the following remarkable advantages:
1. the transmission stability is good: the problem of uneven load distribution in the process of gear fitting transmission is solved through tooth trimming.
2. The noise is low: the installation and manufacturing errors are improved through the modification of the tooth profile, and the noise in the running of the vehicle is reduced.
3. Long fatigue life: the gear stability is improved through the modification of the tooth direction and the modification of the tooth profile, and the fatigue life of the gear is indirectly prolonged through reducing the noise in the meshing process.
The invention is described in further detail below with reference to the figures and the detailed description.
Drawings
FIG. 1 is a main flow chart of the gear modification optimization method of the pure electric vehicle differential gear.
Fig. 2 is a schematic two-dimensional structure diagram of a straight bevel gear in the embodiment.
Fig. 3 is a flow chart of the profile modification step of fig. 1.
Fig. 4 is a flow chart of the step of axial modification in fig. 1.
Fig. 5 is a schematic view of a drum profile.
Table 1 shows 9 sets of profile parameters.
Table 2 shows the 9 sets of tooth crowning parameters.
Detailed Description
As shown in FIG. 1, the method for optimizing the gear modification of the differential of the pure electric vehicle comprises the following steps:
(10) establishing a three-dimensional model of a differential gear: according to parameters of the straight bevel gear, a mathematical equation of the straight bevel gear is combined, and three-dimensional models of the half axle gear and the planetary gear are established;
a two-dimensional schematic of a straight bevel gear is shown in fig. 2.
(20) Single planetary gear profile modification: obtaining a single planetary gear tooth profile modification optimal value through three-dimensional model simulation according to the planetary gear tooth profile modification optimization interval and the tooth profile modification curve formula;
as shown in fig. 3, the (20) tooth profile modifying step comprises:
(21) selecting a tooth profile modification optimization interval: selecting a tooth profile modification optimization interval delta to [0, delta ]max]，
Wherein,
，
in the formula,
Ftb is the circumferential force per tooth width, b is the tooth width of the gear, FtThe circumferential force to which the gear is subjected;
(22) establishing a tooth profile modification curve: determining the tooth profile modification curve according to the following formula,
in the formula, rbIs the base radius, α is the pressure angle, ΔmaxIs the maximum modification amount of the tooth profile, β is a numerical value, L is the length of a double-tooth meshing area, αmaxIs the maximum pressure angle
(23) And (3) model simulation: respectively, take Δ ═ 0, Δ ═ ΔmaxΔ ═ 2maxEstablishing a differential gear model and carrying out simulation to obtain respective simulation results;
(24) secondary model simulation: taking (0, Delta)max/2]Or [ Delta ]max/2，Δmax]The better one of the two results is used as the next optimization interval, and the assumption is that [ Delta ]a1，Δa1]Then, the minimum value, the maximum value and the intermediate value of the interval after optimization are taken to establish threeThe model is simulated, i.e. delta-deltaa1，Δ＝Δa2，Δ＝Δa1+(Δa2-Δa1) 2, and take [ Delta ]a1，Δa1+(Δa2-Δa1)/2]Or [ Delta ]a1+(Δa2-Δa1)/2，Δa2]The better one of the results is used as the optimization interval of the third optimization, and the assumption is that [ delta ]b1，Δb2]；
(25) Three-time model simulation: taking Δ as Δb1，Δ＝Δb2，Δ＝Δb1+(Δb2-Δb1) And/2 establishing three-dimensional models as modification quantities to carry out simulation, and taking [ delta ]b1，Δb1+(Δb2-Δb1)/2]And [ Delta ] andb1+(Δb2-Δb1)/2，Δb2]the simulation result in the two intervals is better taken as the last interval [ Delta ]c1，Δc2]Taking [ Delta ]c1，Δc2]The intermediate value is used as the optimal value delta of the modification of the tooth profile of the planet gearbest。
(30) Single planetary gear tooth axial modification: according to the planetary gear tooth direction modification optimization interval, obtaining a single planetary gear tooth direction modification optimal value through three-dimensional model simulation;
as shown in fig. 4, the (30) axial modification step includes:
(31) selecting a tooth direction modification optimization interval: selecting optimized interval C of tooth direction modification0～[0，25μm]。
(32) And (3) model simulation: respectively taking Cc＝0，Cc25/2 μm and Cc25 mu m is used as the tooth direction modification quantity of the planet gear, and a differential gear model is established for simulation to obtain respective simulation results;
(33) secondary model simulation: taking the interval of [0, 25/2 μm]And [25/2 μm, 25 μm]The better one of the two is used as the next optimization interval, and the assumption is that [ C ]a1，Ca2]. Then get the interval [ Ca1，Ca2]Minimum, median and maximum values of (1), i.e. Cc＝Ca1，Cc＝Ca1+(Ca2-Ca1) /2 and Cc＝Ca2And establishing three-dimensional models for simulation. Taking interval [ Ca1，Ca1+(Ca2-Ca1)/2]And [ Ca1+(Ca2-Ca1)/2，Ca2]The preferred interval in (1) is used as the optimization interval of the third optimization, and is assumed to be [ C ]b1，Cb1]。
(34) Three-time model simulation: get Cc＝Cb1，Cc＝Cb1+(Cb2-Cb1) /2 and Cc＝Cb2Three-dimensional models are established as modification quantities to carry out simulation, and [ C ] is takenb1，Cb1+(Cb2-Cb1)/2]And [ Cb1+(Cb2-Cb1)/2，Cb2]The one with better simulation result in the interval is used as the last interval [ Cc1，Cc2]Taking out [ C ]c1，Cc2]The median value of (A) is used as the optimal value C of the axial modification of the planet gearbest。
FIG. 5 is an example of a drum shape modification entity for modification optimization.
(40) Modification of the gear tooth profile of the full differential: taking the optimal value of the profile modification of the single planetary gear as the total optimal value of the profile modification of the gear of the full differential, equally dividing the optimal value of the profile modification of the single planetary gear into 8 grades, determining 9 groups of parameters of the profile modification of the gear of the differential, carrying out simulation, and taking one group with the optimal simulation result as the optimal solution of the profile modification of the gear of the full differential;
the 9 sets of differential gear tooth profile modification parameters are shown in table 1.
TABLE 1
| Modification of planetary gear tooth profile | Gear profile modification of half axle gear |
| 0 | Δmax |
| Δmax/8 | Δmax*7/8 |
| Δmax*2/8 | Δmax*6/8 |
| Δmax*3/8 | Δmax*5/8 |
| Δmax*4/8 | Δmax*4/8 |
| Δmax*5/8 | Δmax*3/3 |
| Δmax*6/8 | Δmax*2/8 |
| Δmax*7/8 | Δman*1/8 |
| Δmax | 0 |
(50) Axial modification of the gear of the full differential: and taking the tooth direction modification optimal value of the single planetary gear as the total tooth direction modification optimal value of the full differential gear, equally dividing the tooth direction modification optimal value of the single planetary gear into 8 levels, determining 9 groups of differential gear tooth direction modification parameters, performing simulation, and taking one group with the optimal simulation result as the optimal solution of the tooth direction modification of the full differential gear.
The 9 sets of differential gear tooth profile parameters are shown in table 2.
TABLE 2
Claims (3)
1. A pure electric vehicle differential gear modification optimization method is characterized by comprising the following steps:
(10) establishing a three-dimensional model of a differential gear: according to parameters of the straight bevel gear, a mathematical equation of the straight bevel gear is combined, and three-dimensional models of the half axle gear and the planetary gear are established;
(20) single planetary gear profile modification: obtaining a single planetary gear tooth profile modification optimal value through three-dimensional model simulation according to the planetary gear tooth profile modification optimization interval and the tooth profile modification curve formula;
(30) single planetary gear tooth axial modification: according to the planetary gear tooth direction modification optimization interval, obtaining a single planetary gear tooth direction modification optimal value through three-dimensional model simulation;
(40) modification of the gear tooth profile of the full differential: taking the optimal value of the profile modification of the single planetary gear as the total optimal value of the profile modification of the gear of the full differential, equally dividing the optimal value of the profile modification of the single planetary gear into 8 grades, determining 9 groups of parameters of the profile modification of the gear of the differential, carrying out simulation, and taking one group with the optimal simulation result as the optimal solution of the profile modification of the gear of the full differential;
(50) axial modification of the gear of the full differential: and taking the tooth direction modification optimal value of the single planetary gear as the total tooth direction modification optimal value of the full differential gear, equally dividing the tooth direction modification optimal value of the single planetary gear into 8 levels, determining 9 groups of differential gear tooth direction modification parameters, performing simulation, and taking one group with the optimal simulation result as the optimal solution of the tooth direction modification of the full differential gear.
2. The gear modification optimization method of claim 1, wherein the (20) tooth profile modification step comprises:
(21) selecting a tooth profile modification optimization interval: selecting a tooth profile modification optimization interval delta to [0, delta ]max]，
Wherein,
Δmax＝(4+0.05Ft/b)±4，
in the formula,
Ftb is the circumferential force per tooth width, b is the tooth width of the gear, FtThe circumferential force to which the gear is subjected;
(22) establishing a tooth profile modification curve: determining the tooth profile modification curve according to the following formula,
in the formula, rbIs the base radius, α is the pressure angle, ΔmaxIs the maximum modification amount of the tooth profile, β is a numerical value, L is the length of a double-tooth meshing area, αmaxIs the maximum pressure angle
(23) And (3) model simulation: respectively, take Δ ═ 0, Δ ═ ΔmaxΔ ═ 2maxEstablishing a differential gear model and carrying out simulation to obtain respective simulation results;
(24) secondary model simulation: take [0, Deltamax/2]Or [ Delta ]max/2，Δmax]The better one of the two results is used as the next optimization interval, and the assumption is that [ Delta ]a1，Δa2]Then, three models are established for simulation by taking the minimum value, the maximum value and the intermediate value of the interval after optimization, namely, delta is equal to deltaa1，Δ＝Δa2，Δ＝Δa1+(Δa2-Δα1) 2, and take [ Delta ]a1，Δa1+(Δa2-Δa1)/2]Or [ Delta ]a1+(Δa2-Δa1)/2，Δa2]The better one of the results is used as the optimization interval of the third optimization, and the assumption is that [ delta ]b1，Δb2]；
(25) Three-time model simulation: taking Δ as Δb1，Δ＝Δb2，Δ＝Δb1+(Δb2-Δb1) And/2 establishing three-dimensional models as modification quantities to carry out simulation, and taking [ delta ]b1，Δb1+(Δb2-Δb1)/2]And [ Delta ] andb1+(Δb2-Δb2)/2，Δb2]the simulation result in the two intervals is better taken as the last interval [ Delta ]c1，Δc2]Taking [ Delta ]c1，Δc2]The intermediate value is used as the optimal value delta of the modification of the tooth profile of the planet gearbest。
3. The gear shaping optimization method of claim 1, wherein the (30) axial shaping step comprises:
(31) selecting a tooth direction modification optimization interval: selecting optimized interval C of tooth direction modification0～[0，25μm]。
(32) And (3) model simulation: respectively taking Ce＝0，Cc25/2 μm and Ce25 mu m is used as the tooth direction modification quantity of the planet gear, and a differential gear model is established for simulation to obtain respective simulation results;
(33) secondary model simulation: taking the interval of [0, 25/2 μm]And [25/2 μm, 25 μmm]The better one of the two is used as the next optimization interval, and the assumption is that [ C ]a1，Ca2]. Then get the interval [ Ca1，Ca2]Minimum, median and maximum values of (1), i.e. Cc＝Ca1，Cc＝Ca1+(Ca2-Ca1) /2 and Cc＝Ca2And establishing three-dimensional models for simulation. Taking interval [ Ca1，Ca2+(Ca2-Ca1)/2]And [ Ca1+(Ca2-Ca1)/2，Ca2]The preferred interval in (1) is used as the optimization interval of the third optimization, and is assumed to be [ C ]b1，Cb2]。
(34) Three-time model simulation: get Cc＝Cb1，Ce＝Cb1+(Cb2-Cb1) /2 and Cc＝Cb2Three-dimensional models are established as modification quantities to carry out simulation, and [ C ] is takenb1，Cb2+(Cb2-Cb1)/2]And [ Cb1+(Cb2-Cb1)/2，Cb2]The one with better simulation result in the interval is used as the last interval [ Cc1，Cc2]Taking out [ C ]c1，Cc2]The median value of (A) is used as the optimal value C of the axial modification of the planet gearbest。
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110630719A (en) * | 2019-08-29 | 2019-12-31 | 南京理工大学 | Differential gear modification optimization method |
| CN110671483A (en) * | 2019-09-27 | 2020-01-10 | 贵州群建精密机械有限公司 | Machining method for reducing gear noise of electric scooter |
| CN114896741A (en) * | 2022-06-27 | 2022-08-12 | 重庆青山工业有限责任公司 | Method for rapidly optimizing design parameters of new energy differential assembly |
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| CN102853056A (en) * | 2012-08-29 | 2013-01-02 | 江苏太平洋精锻科技股份有限公司 | Correction arc bevel gear supporting automobile differential mechanism |
| CN108644342A (en) * | 2018-05-08 | 2018-10-12 | 武汉理工大学 | The method for building up of not rounded bevel gear limited slip differential kinetic model |
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| CN102853056A (en) * | 2012-08-29 | 2013-01-02 | 江苏太平洋精锻科技股份有限公司 | Correction arc bevel gear supporting automobile differential mechanism |
| CN108644342A (en) * | 2018-05-08 | 2018-10-12 | 武汉理工大学 | The method for building up of not rounded bevel gear limited slip differential kinetic model |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110630719A (en) * | 2019-08-29 | 2019-12-31 | 南京理工大学 | Differential gear modification optimization method |
| CN110671483A (en) * | 2019-09-27 | 2020-01-10 | 贵州群建精密机械有限公司 | Machining method for reducing gear noise of electric scooter |
| CN114896741A (en) * | 2022-06-27 | 2022-08-12 | 重庆青山工业有限责任公司 | Method for rapidly optimizing design parameters of new energy differential assembly |
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Effective date of registration: 20221207 Address after: No. 91, Jiangyan Avenue, Jiangyan District, Taizhou, Jiangsu 225599 Patentee after: JIANGSU PACIFIC PRECISION FORGING Co.,Ltd. Address before: 210094 No. 200, Xiaolingwei, Jiangsu, Nanjing Patentee before: NANJING University OF SCIENCE AND TECHNOLOGY Patentee before: JIANGSU PACIFIC PRECISION FORGING Co.,Ltd. |