CN107562972A - A kind of differential carrier body stress and stiffness analysis method - Google Patents
A kind of differential carrier body stress and stiffness analysis method Download PDFInfo
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- CN107562972A CN107562972A CN201610522022.3A CN201610522022A CN107562972A CN 107562972 A CN107562972 A CN 107562972A CN 201610522022 A CN201610522022 A CN 201610522022A CN 107562972 A CN107562972 A CN 107562972A
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Abstract
The present invention relates to a kind of differential carrier body stress and stiffness analysis method, comprise the following steps：By static CAE analysis model, the CAE stress models of main pinion are established；Add part material attribute, tri- directional stiffness numerical value of X, Y, Z of differential bearing and stud, diff. bearing cap and beat pretightning force caused by moment of torsion, under the maximum input torque of engine, calculate the component in tri- directions of X, Y, Z caused by passive bevel gear engagement, calculate under stressing conditions, the magnitude of misalignment of passive bevel gear meshing point, i.e., deflection caused by passive bevel gear.Beneficial effects of the present invention are：The deflection of housing can be calculated by this analysis method, and housing is optimized, and then reduces master and subtracts the roar occurred during acceleration and slide caused gear noise, improves the interior noise of vehicle, improves riding property.
Description
Technical field
The invention belongs to automobile manufacturing field, and in particular to a kind of differential carrier body stress and stiffness analysis method.
Background technology
In the prior art, some vehicles newly developed master when accelerating subtracts and sends roar, and gear noise is bright when sliding
It is aobvious, in-car test noise severe overweight, the riding poor-performing of vehicle.
Existing master subtracts assembly and develops early stage, borrows first use small displacement always, the design concept of the engine of small moment of torsion, knot
Whether structure borrows existing structure substantially, does not calculate and match in detail type selecting, have ignored and meet first with the use of exploitation vehicle
It is required that.
During existing exploitation vehicle, master, engaged by tooth when testing (test engagement trace, TE values and gear noise), it is resonable
Carried out by installation is lower, ignore gear support to the main influence for subtracting assembly.
The content of the invention
The present invention proposes a kind of differential carrier body stress and stiffness analysis method, establishes the main CAE analysis model for subtracting assembly,
The stress model of gear and the assembly relation of parts are analyzed, calculates the rigidity value and stress value of each part；Analysis calculates differential
Stress deformation situation be present during device housing circle rotation, therefore be changed to circumference symmetrical structure, improve the magnitude of misalignment of gear engagement；Solve
The installation span problem of differential mechanism；Solve differential casing wall thickness and perforate distribution；Optimize differential casing strengthening rib strip
Shape and position.
The technical proposal of the invention is realized in this way：
A kind of differential carrier body stress and stiffness analysis method, comprise the following steps：By static CAE analysis model, build
The CAE stress models of vertical main pinion；Add part material attribute, tri- directional stiffness numerical value of X, Y, Z and difference of differential bearing
Fast device bolt of bearing cap beats pretightning force caused by moment of torsion, under the maximum input torque of engine, calculates passive bevel gear and nibbles
The component in tri- directions of X, Y, Z, is calculated under stressing conditions caused by conjunction, the magnitude of misalignment of passive bevel gear meshing point, i.e. quilt
Deflection caused by dynamic bevel gear.
Further, the part material attribute include differential casing material properties, passive bevel gear material properties and
Differential bearing material properties.
Further, the material properties include modulus of elasticity and Poisson's ratio.
Further, the deflection according to caused by passive bevel gear, the deflection of differential casing can be analyzed.
Further, according to the deflection of differential casing, the weak part of differential casing is found out, to differential casing
Optimize.
Further, according to the weak part of differential casing, the Optimized Measures of differential casing are included to differential mechanism
The arrangement of housing reinforcement optimizes, the installation span to differential mechanism optimizes and the wall thickness to differential casing and perforate
Distribution optimizes.
Beneficial effects of the present invention are：
The deflection of housing can be calculated by this analysis method, and housing is optimized, and then reduces main subtract and adds
The roar that occurs when fast and caused gear noise is slided, improve the interior noise of vehicle, improve riding property.
Brief description of the drawings
In order to illustrate more clearly about the embodiment of the present invention or technical scheme of the prior art, below will be to embodiment or existing
There is the required accompanying drawing used in technology description to be briefly described, it should be apparent that, drawings in the following description are only this
Some embodiments of invention, for those of ordinary skill in the art, on the premise of not paying creative work, can be with
Other accompanying drawings are obtained according to these accompanying drawings.
Fig. 1 is the mounting structure schematic diagram of differential mechanism；
Fig. 2 is the structural representation of the differential casing after optimization.
In figure：
1st, differential casing；2nd, differential bearing；3rd, stud, diff. bearing cap；4th, passive bevel gear；5th, reinforcement.
Embodiment
Below in conjunction with the accompanying drawing in the embodiment of the present invention, the technical scheme in the embodiment of the present invention is carried out clear, complete
Site preparation describes, it is clear that described embodiment is only part of the embodiment of the present invention, rather than whole embodiments.It is based on
Embodiment in the present invention, those of ordinary skill in the art are obtained every other under the premise of creative work is not made
Embodiment, belong to the scope of protection of the invention.
As shown in figure 1, differential carrier body stress and stiffness analysis method, comprise the following steps：Pass through static CAE analysis mould
Type, establish the CAE stress models of main pinion；Add the material category of differential casing 1, passive bevel gear 4 and differential bearing 2
Property, tri- directional stiffness numerical value of X, Y, Z of differential bearing 2 and stud, diff. bearing cap 3 beat pretightning force caused by moment of torsion,
Under the maximum input torque of engine, the component in tri- directions of X, Y, Z caused by passive bevel gear engagement is calculated, is calculated
Under stressing conditions, the magnitude of misalignment of passive bevel gear meshing point, i.e., deflection caused by passive bevel gear.
Application example
(1) complete differential assembly model for dynamic analysis is established using masta softwares, imports Gleason gear processed file
Spa files ensure main consistent with real vehicle by tooth.Engine driveshaft input input peak torque 145Nm, calculate by
The component in tri- directions of X, Y, Z caused by dynamic bevel gear engagement：Force of periphery 24100.34N, axial thrust load 27449.84 and footpath
To component 3945.961N.
(2) complete differential assembly model is established using abaqus softwares, CAE analysis needs to input the material category of part
Property, the material of differential casing is cast iron, and the material property of cast iron, modulus of elasticity 162GPa, Poisson are inputted in CAE software
Than being steel for the material of 0.293, passive bevel gear and differential bearing Internal and external cycle, the modulus of elasticity of steel is 210GPa, Poisson's ratio
For 0.3.Model includes the differential bearing for considering three directional stiffness, can be simulated in finite element analysis using spring unit
Bearing, the rigidity of certain vehicle bearing are X=2037000N/mm, Y=1875000N/mm, Z=280900N/mm, differential bearing
Lid applies pretightning force according to real vehicle state, is connected with by tooth and poor shell, bearing and bearing cap, bearing and poor shell, by tooth and
The parts such as poor shell in the light of actual conditions establish contact, and the component in three directions is loaded at passive bevel gear meshing point.Finally may be used
By analysis go on business shell deflection (on the basis of main tooth meshing point, offset direction vehicle be backward+X, to the right+Y, it is upward be+Z)
X=0.15mm, y=0.0218mm, z=0.156mm.
There is stress deformation situation in analysis, therefore be changed to circumference symmetrical structure when calculating differential casing circle rotation, improve
The magnitude of misalignment of gear engagement.As shown in Fig. 2 the differential mechanism casing structure schematic diagram after optimization, reinforcement are circumferentially arranged symmetrically.
The foregoing is merely illustrative of the preferred embodiments of the present invention, is not intended to limit the invention, all essences in the present invention
God any modification, equivalent substitution and improvements made etc., should be included in the scope of the protection with principle.
Claims (6)
1. a kind of differential carrier body stress and stiffness analysis method, it is characterised in that comprise the following steps：Pass through static CAE points
Model is analysed, establishes the CAE stress models of main pinion；Add part material attribute, tri- directional stiffness of X, Y, Z of differential bearing
Numerical value and stud, diff. bearing cap beat pretightning force caused by moment of torsion, and under the maximum input torque of engine, it is passive to calculate
The component in tri- directions of X, Y, Z, is calculated under stressing conditions, the dislocation of passive bevel gear meshing point caused by bevel gear engagement
Amount, i.e., deflection caused by passive bevel gear.
2. differential carrier body stress according to claim 1 and stiffness analysis method, it is characterised in that：The part material
Attribute includes differential casing material properties, passive bevel gear material properties and differential bearing material properties.
3. differential carrier body stress according to claim 1 and stiffness analysis method, it is characterised in that：The material properties
Including modulus of elasticity and Poisson's ratio.
4. differential carrier body stress and stiffness analysis method according to claim any one of 1-3, it is characterised in that：According to
Deflection caused by passive bevel gear, the deflection of differential casing can be analyzed.
5. differential carrier body stress according to claim 4 and stiffness analysis method, it is characterised in that：According to differential carrier
The deflection of body, the weak part of differential casing is found out, differential casing is optimized.
6. differential carrier body stress according to claim 5 and stiffness analysis method, it is characterised in that：According to differential carrier
The weak part of body, the Optimized Measures of differential casing are included optimizing, to difference the arrangement of differential casing reinforcement
The installation span of fast device optimizes and the wall thickness of differential casing and perforate distribution is optimized.
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Cited By (8)
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| CN109829185A (en) * | 2018-12-13 | 2019-05-31 | 铠龙东方汽车有限公司 | A kind of nut loosening analysis method based on pretightning force |
| CN110188504A (en) * | 2019-06-11 | 2019-08-30 | 武汉理工大学 | The main reducing gear driven gear support stiffness analysis method of reducing gearbox and rear axle housing |
| JP2019163838A (en) * | 2018-03-20 | 2019-09-26 | トヨタ自動車株式会社 | Case component of transaxle |
| CN110567626A (en) * | 2019-09-30 | 2019-12-13 | 华中光电技术研究所（中国船舶重工集团有限公司第七一七研究所） | Indirect bearing pretightening force measuring method and system |
| CN112052510A (en) * | 2019-12-12 | 2020-12-08 | 格特拉克（江西）传动系统有限公司 | Method for checking slip risk of bolted connection of differential mechanism based on dynamic load |
| CN112747102A (en) * | 2020-12-31 | 2021-05-04 | 安徽江淮汽车集团股份有限公司 | Simulation calculation method, computer, and storage medium |
| CN113111462A (en) * | 2021-04-21 | 2021-07-13 | 中国第一汽车股份有限公司 | Method for forecasting limit bearing capacity of differential shell |
| CN115630454A (en) * | 2022-10-21 | 2023-01-20 | 南京工业大学 | Precise modeling method for Grarison spiral bevel gear |
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| JP7000216B2 (en) | 2018-03-20 | 2022-02-04 | トヨタ自動車株式会社 | Transaxle case parts |
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| CN110188504A (en) * | 2019-06-11 | 2019-08-30 | 武汉理工大学 | The main reducing gear driven gear support stiffness analysis method of reducing gearbox and rear axle housing |
| CN110188504B (en) * | 2019-06-11 | 2020-04-17 | 武汉理工大学 | Method for analyzing support rigidity of driven gear of main reducer of reducer shell and rear axle housing |
| CN110567626A (en) * | 2019-09-30 | 2019-12-13 | 华中光电技术研究所（中国船舶重工集团有限公司第七一七研究所） | Indirect bearing pretightening force measuring method and system |
| CN110567626B (en) * | 2019-09-30 | 2021-05-11 | 华中光电技术研究所（中国船舶重工集团有限公司第七一七研究所） | Indirect bearing pretightening force measuring method and system |
| CN112052510A (en) * | 2019-12-12 | 2020-12-08 | 格特拉克（江西）传动系统有限公司 | Method for checking slip risk of bolted connection of differential mechanism based on dynamic load |
| CN112052510B (en) * | 2019-12-12 | 2024-04-05 | 麦格纳动力总成(江西)有限公司 | Dynamic load-based differential mechanism bolting slip risk checking method |
| CN112747102A (en) * | 2020-12-31 | 2021-05-04 | 安徽江淮汽车集团股份有限公司 | Simulation calculation method, computer, and storage medium |
| CN113111462A (en) * | 2021-04-21 | 2021-07-13 | 中国第一汽车股份有限公司 | Method for forecasting limit bearing capacity of differential shell |
| CN113111462B (en) * | 2021-04-21 | 2022-06-07 | 中国第一汽车股份有限公司 | Method for forecasting limit bearing capacity of differential shell |
| CN115630454A (en) * | 2022-10-21 | 2023-01-20 | 南京工业大学 | Precise modeling method for Grarison spiral bevel gear |
| CN115630454B (en) * | 2022-10-21 | 2023-10-20 | 南京工业大学 | Method for accurately modeling Glison spiral bevel gear |
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