CN110532584A - A kind of Non-carrying type body in white light weight method based on relative sensitivity - Google Patents
A kind of Non-carrying type body in white light weight method based on relative sensitivity Download PDFInfo
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Abstract
The Non-carrying type body in white light weight method based on relative sensitivity that the invention discloses a kind of, mainly by using Beam unit simulation wheel center point position when constraint Non-carrying type white body, thus reduced rigidity phenomenon and by a variety of direct sensitivity carry out weight operations obtain be used for after relative sensitivity it is dimensionally-optimised；The present invention solves the problems, such as design variable lightweight component due to caused by the weight differential screening problem for crossing deflection constraint and the sensitivity to multiple responses when Non-carrying type white body Rigidity Calculation.
Description
Technical field:
The invention belongs to automotive body structure optimization design field, in particular to a kind of non-bearing based on relative sensitivity
Formula body in white light weight method.
Background technique:
Vehicle mass reduction becomes current vehicle body design industry development direction.According to statistics, automobile is every reduces total weight
10%, fuel consumption will reduce 6%-8%, reduce discharge 5%-6%.Automotive light weight technology is not so simple that increased or decrease portion
The thickness of part, or increase and decrease component.But under the premise of guaranteeing the performances such as original body stiffness, mode, one kind is searched out most
Excellent solution.The structure that automobile is carried out in terms of dimensionally-optimised, shape optimum, topography optimization etc. are multidisciplinary is improved.
Non-carrying type white body is a kind of body structure being mounted on vehicle frame.For Non-carrying type white body, existing point
Analysis technology mostly analyzes white body together with body frame structure for automotive, to increase the time cost of analytic process.
Meanwhile Non-carrying type white body only undertakes a part of rigidity of the vehicle and absorption of vibrations, and load is added to white vehicle
The problem of vehicle frame and vehicle body spend rigidity of the vehicle and modal contribution can be ignored in body and the common research object of vehicle frame.It is how quasi-
Really individually the performance of research Non-carrying type white body becomes a key technology.
The information disclosed in the background technology section is intended only to increase the understanding to general background of the invention, without answering
When being considered as recognizing or imply that the information constitutes the prior art already known to those of ordinary skill in the art in any form.
Summary of the invention:
The Non-carrying type body in white light weight method based on relative sensitivity that the purpose of the present invention is to provide a kind of, thus
Overcome above-mentioned defect in the prior art.
To achieve the above object, the present invention provides a kind of Non-carrying type body in white light weight side based on relative sensitivity
Method carries out in accordance with the following steps:
Step 1, according to CATIA three-dimension modeling finite element analysis model；
Step 2, Non-carrying type white body bending stiffness torsion stiffness and model analysis are carried out；
Step 3, rigidity and Modal sensitivity response analysis model are established respectively；
Step 4, Relative sensitivity analysis is carried out on the basis of sensitivity analysis and selects lightweight component；
Step 5, dimensionally-optimised to the component progress multiple target filtered out；
Step 6, the Non-carrying type white body after lightweight is subjected to performance verification.
The technical solution that the present invention further limits are as follows:
Preferably, in above-mentioned technical proposal, step 1 specifically:
1.1 need to meet according to CATIA three-dimension modeling finite element model, mesh quality: warpage or warp <
15°；Skewness<60°；Jacobian≧0.6；Ratio of length to width≦5；Minimum internal
Angle of CQUAD4=45 °；Maxmum internal angle of CQUAD4=135 °；Minimum internal
Angle of CTRIA3=15 °；Maxmum internal angle of CTRIA3=105 °；
1.2 thin plate junction solder joint units use ace (general) type；Place is bolted using RBE3 unit；Vehicle frame
Vehicle body junction and suspension installation point use RIGID unit；
Bilayer washer unit is used around 1.3 bolts hole, plate sheet welding marginal portion mesh-density is bilayer；
1.4 assign different material properties to component according to part library table.
Preferably, in above-mentioned technical proposal, step 2 specifically:
2.1 pairs of Non-carrying type white bodies carry out Free Modal Analysis, that is, boundary condition and load is not added；Its mathematical model
Are as follows:
Wherein K, C, M are the stiffness matrix, damping matrix and mass matrix of system respectively；X and F
It is the motion vector and excitation force vector of system respectively, respectively indicates are as follows:
X=[x1x2......xr......xN]Γ,
F=[f1f2......fr......fN]Γ；
Two vectors are decoupled, need to carry out certain conversion in Uncoupled procedure；I.e. physical coordinates mode
Coordinate replaces, final to realize solution of equations coupling, obtains the mode and the vibration shape under each frequency；
2.2 pairs of Non-carrying type white bodies carry out Bending Stiffness Analysis, first setting boundary condition；Constrained is white body
With vehicle frame front or so two simulating wheel installation points of two simulating wheel points and Rear frame vehicle body；The way of restraint are as follows: left front company
Connect place's constraint Z-direction translational degree of freedom；Right preceding junction constraint Y and Z-direction translational degree of freedom；Left back junction constraint X and Z-direction translation
Freedom degree；Junction constraint Y and Z-direction translational degree of freedom behind the right side；Load setting are as follows: adopted at horizontal bar in the middle part of the Non-carrying type white body
It is loaded with rigid unit concentrfated load mode or so；
2.3 pairs of Non-carrying type white bodies carry out torsion stiffness analysis, first setting boundary condition；Constrained is front of the car
Two installation points in vehicle frame junction middle position and last vehicle frame vehicle body；The way of restraint are as follows: constraint foreside bodywork vehicle frame installation point
Middle part Z-direction Pingdu freedom degree；Constrain rear portion vehicle body frames installation point six direction whole freedom degree；Load setting are as follows: in front
Vehicle body frames installation point left-right position loads opposite a pair of of the torque of the size same direction.
Preferably, in above-mentioned technical proposal, in step 3, sensitivity analysis is carried out by design variable of panel thickness d；Spirit
The citation form of basis of sensitivity analysis are as follows:
Wherein, X is the vector of body structure design parameter composition at reference point；X is the variation of body structure design parameter,
Default value is the 1% of the difference of upper and lower limit；E is the vector with X with dimension；U is body structure performance parameter；Stiffness Sensitivity
Mathematical model is by Rigidity Calculation formula:
[K]n*n{u}n*l={ F }n*l,
Wherein, [K]n*nFor the overall stiffness of research object；{u}n*lFor the motion vector of analysis model；{F}n*lFor analysis
The external applied load vector of model.Above formula can obtain after seeking local derviation to design variable d, that is, thickness:
[K,d]n*n{μ}n*l+[K]n*n{u,d}n*l=F,d}n*l={ 0 }n*l,
μ,d}=- [K]n*n -1[K,d]n*n{μ}n*l,
Wherein, [K,d]n*n -1It is each unit for the global stiffness matrix of analysis model overall stiffness inverse matrix structural model
The corresponding rank matrix that expands is formed by stacking；
It, can be by a kind of substitution of measurement point being displaced as stiffness response in Stiffness Sensitivity calculating；It is set in load
Set it is constant under conditions of, displacement variation be rigidity variation；
Modal sensitivity is determined by material properties and thickness, with the minimum target of white body quality；First-order flexure mode
It is constraint greater than original value, is that response is analyzed with quality and modal frequency.
Preferably, in above-mentioned technical proposal, step 4 specifically:
By step 3 calculate separately out about bending stiffness, torsion stiffness, single order torsion mode, quality sensitivity after root
According to relative sensitivity defined formula:
Wherein SwFor the direct sensitivity of quality, SB isDirect bending stiffness sensitivity, StFor direct torsion stiffness sensitivity, Sf
For direct Modal sensitivity.
Preferably, in above-mentioned technical proposal, step 5 specifically: by step 4 gained relative sensitivity as a result, selecting can mention
The component that high body stiffness and Modal Performances and body quality are not significantly increased；Select optimal Latin hypercube method by step 2
In each design variable performance carry out experimental design；First-order kernel surface model is established after obtaining test sample point:
In formula, a is multinomial coefficient；xjFor design variable；Q is design variable number；
Then coefficient of multiple correlation R is utilized2Carry out the accuracy of auth response face fitting.Its is defined as:
R2=1-QC/QZ,
In formula, QCFor residual deviation quadratic sum；QZFor sum of square of deviations；
Finally, single order torsion mode, bending stiffness, torsion stiffness are constraint with body quality minimum target；Using grain
Swarm optimization carries out multiple-objection optimization.The wherein general type of particle swarm algorithm are as follows:
vid=w × vid+c1×rand()×(pid-xid)+c2×Rand()×(pgd-xid)
xid=xid+vid,
In formula, wherein w is inertia weight, c1And c2For aceleration pulse, rand () and Rand () are two in [0,1] range
In the random value that changes；First item formula is Inertia in first formula, and particle is made to have the tendency that expanded search space；Section 2
For " cognition " item, thinking of the particle to improvement direction itself is indicated；Section 3 is " society " item, indicates interparticle optimal information
It is shared.
Preferably, in above-mentioned technical proposal, step 6 specifically: by carry out it is dimensionally-optimised after component assign attribute again
Afterwards, static rigidity and model analysis are re-started according to the method for step 2, whether is the white body performance after comparison is dimensionally-optimised
Decline.
Compared with prior art, the invention has the following beneficial effects:
The present invention accurately calculates the white vehicle of Non-carrying type by establishing Non-carrying type white body deflection constraint model
The basic performances such as bending stiffness, torsion stiffness, the mode of body vehicle frame above section.White body Sensitivity Analysis is established, and
It is dimensionally-optimised that multiple target has been carried out by the method based on response surface model.Research and development process is shortened, it is white to improve Non-carrying type
The light-weighted reliability of vehicle body.
Detailed description of the invention:
Fig. 1 is a kind of flow diagram of the Non-carrying type body in white light weight method based on relative sensitivity of the present invention.
Fig. 2 is Non-carrying type body-in-white structure schematic diagram of the present invention.
Fig. 3 is the flow diagram of sensitivity analysis of the present invention.
Specific embodiment:
Specific embodiments of the present invention will be described in detail below, it is to be understood that protection scope of the present invention is not
It is restricted by specific implementation.
Unless otherwise explicitly stated, otherwise in entire disclosure and claims, term " includes " or its change
Changing such as "comprising" or " including " etc. will be understood to comprise stated element or component, and not exclude other members
Part or other component parts.
A kind of Non-carrying type body in white light weight method based on relative sensitivity, specific steps are as follows:
Step 1: a) according to CATIA three-dimension modeling finite element model, mesh quality needs to meet: warpage or
warp<15°；Skewness<60°；Jacobian≧0.6；Ratio of length to width≦5；Minimum
Internal angle of CQUAD4=45 °；Maxmum internal angle of CQUAD4=135 °；Minimum
Internal angle of CTRIA3=15 °；Maxmum internal angle of CTRIA3=105 °.
B) solder joint unit in thin plate junction uses ace (general) type；Place is bolted using RBE3 unit；Vehicle frame
Vehicle body junction and suspension installation point use RIGID unit.
C) bilayer washer unit is used around bolt hole, plate sheet welding marginal portion mesh-density is bilayer.
D) different material properties are assigned to component according to part library table
A) step 2: Free Modal Analysis is carried out to Non-carrying type white body, that is, boundary condition and load is not added.It is counted
Learn model are as follows:
Wherein K, C, M are the stiffness matrix, damping matrix and mass matrix of system respectively.X and F
It is the motion vector and excitation force vector of system respectively, respectively indicates are as follows:
X=[x1x2......xr......xN]Γ
F=[f1f2......fr......fN]Γ,
Two vectors are decoupled, need to carry out certain conversion in Uncoupled procedure.I.e. physical coordinates mode
Coordinate replaces, final to realize solution of equations coupling, obtains the mode and the vibration shape under each frequency.
Step 2: carrying out Bending Stiffness Analysis to Non-carrying type white body, first setting boundary condition.Constrained is white
Two simulated wheel points of two simulated wheel points of vehicle body and vehicle frame front or so and Rear frame vehicle body.The way of restraint are as follows: left front company
Connect place's constraint Z-direction translational degree of freedom；Right preceding junction constraint Y and Z-direction translational degree of freedom；Left back junction constraint X and Z-direction translation
Freedom degree；Junction constraint Y and Z-direction translational degree of freedom behind the right side.Load setting are as follows: adopted at horizontal bar in the middle part of the Non-carrying type white body
It is loaded with rigid unit concentrfated load mode or so.
Torsion stiffness analysis is carried out to Non-carrying type white body, first setting boundary condition.Constrained is front of the car vehicle
Two installation points in frame junction middle position and last vehicle frame vehicle body.The way of restraint are as follows: in constraint foreside bodywork vehicle frame installation point
Portion's Z-direction Pingdu freedom degree.Constrain rear portion vehicle body frames installation point six direction whole freedom degree.Load setting are as follows: in front vehicle
Body vehicle frame installation point left-right position loads opposite a pair of of the torque of the size same direction.
Step 3: sensitivity analysis is carried out by design variable of panel thickness d.The citation form of sensitivity analysis are as follows:
Wherein, X is the vector of body structure design parameter composition at reference point；X is the variation of body structure design parameter,
Default value is the 1% of the difference of upper and lower limit；E is the vector with X with dimension；U is body structure performance parameter.Stiffness Sensitivity
Mathematical model is by Rigidity Calculation formula:
[K]n*n{u}n*l={ F }n*l,
Wherein, [K]n*nFor the overall stiffness of research object；{u}n*lFor the motion vector of analysis model；{F}n*lFor analysis
The external applied load vector of model.Above formula can obtain after seeking local derviation to design variable d, that is, thickness:
[K,d]n*n{μ}n*l+[K]n*n{u,d}n*l=F,d}n*l={ 0 }n*l
μ,d}=- [K]n*n -1[K,d]n*n{μ}n*l,
Wherein, [K,d]n*n -1It is each for the global stiffness matrix of analysis model overall stiffness inverse matrix structural model
The corresponding expansion rank matrix of unit is formed by stacking.
It, can be by a kind of substitution of measurement point being displaced as stiffness response in Stiffness Sensitivity calculating.It is set in load
Set it is constant under conditions of, the variation of displacement can be used as the constraint of Stiffness Sensitivity.
Modal sensitivity is determined by material properties and thickness, with the minimum target of white body quality.First-order flexure mode
It is constraint greater than original value, is that response is analyzed with quality and modal frequency.
Step 4: by step 3 calculate separately out about bending stiffness, torsion stiffness, single order torsion mode, quality it is sensitive
According to relative sensitivity defined formula after degree:
Wherein SwFor the direct sensitivity of quality, SB isDirect bending stiffness sensitivity, StFor direct torsion stiffness sensitivity, Sf
For direct Modal sensitivity.
Step 5: by step 4 gained relative sensitivity as a result, body stiffness and Modal Performances and vehicle body matter can be improved by selecting
Measure the component not being significantly increased.It selects optimal Latin hypercube method that the performance of design variable each in step 2 is carried out test to set
Meter.First-order kernel surface model is established after obtaining test sample point:
In formula, a is multinomial coefficient；xjFor design variable；Q is design variable number.
Then coefficient of multiple correlation R is utilized2Carry out the accuracy of auth response face fitting.Its is defined as:
R2=1-QC/QZ
In formula, QCFor residual deviation quadratic sum；QZFor sum of square of deviations.
Finally, single order torsion mode, bending stiffness, torsion stiffness are constraint with body quality minimum target.Using grain
Swarm optimization carries out multiple-objection optimization.The wherein general type of particle swarm algorithm are as follows:
vid=w × vid+c1×rand()×(pid-xid)+c2×Rand()×(pgd-xid)
xid=xid+vid,
In formula, wherein w is inertia weight, c1And c2For aceleration pulse, rand () and Rand () are two in [0,1] range
In the random value that changes.First item formula is Inertia in first formula, and particle is made to have the tendency that expanded search space；Section 2
For " cognition " item, thinking of the particle to improvement direction itself is indicated；Section 3 is " society " item, indicates interparticle optimal information
It is shared.
Step 6: by carry out it is dimensionally-optimised after component assign attribute again after, re-started according to the method for step 2 quiet
State rigidity and model analysis.Compare it is dimensionally-optimised after white body performance whether decline.
Elaborate below with reference to the embodiment of the present invention, the present embodiment under the premise of the technical scheme of the present invention into
Row is implemented, and the detailed implementation method and specific operation process are given, but protection scope of the present invention is not limited to following realities
Apply example.
Embodiment
As shown in Figure 1, a kind of Non-carrying type body in white light weight method based on relative sensitivity, it specifically includes following
Step:
Step 1: establishing Non-carrying type white body finite element model, and mesh quality needs to meet: warpage or warp <
15°；Skewness<60°；Jacobian≧0.6；Ratio of length to width≦5；Minimum internal
Angle of CQUAD4=45 °；Maxmum internal angle of CQUAD4=135 °；Minimum internal
Angle of CTRIA3=15 °；Maxmum internal angle of CTRIA3=105 °.
B) solder joint unit in thin plate junction uses ace (general) type；Place is bolted using RBE3 unit；Vehicle frame
Vehicle body junction and suspension installation point use RIGID unit.
C) bilayer washer unit is used around bolt hole, plate sheet welding marginal portion mesh-density is bilayer.
D) different material properties are assigned to component according to part library table
Step 2: progress Free Modal Analysis first.This model obtains the first six rank modal analysis result such as following table.
| Order | Frequency | The vibration shape |
| 1 | 16.2Hz | Vehicle body integrally reverses |
| 2 | 19.8Hz | Front section of vehicle frame and rear cabin are reversed |
| 3 | 23.2Hz | The front lateral bending of vehicle body entirety |
| 4 | 25.2Hz | Vehicle body entirety first-order flexure |
| 5 | 27.7Hz | The roof surge of driver's cabin front |
| 6 | 31.5Hz | Driver's cabin middle vehicle surge |
Secondly Bending Stiffness Analysis is carried out to Non-carrying type white body, first setting boundary condition.Constrained is white vehicle
Two installation points of two installation points of body and vehicle frame front or so and last vehicle frame vehicle body.The way of restraint are as follows: left front junction constrains Z
To translational degree of freedom；Right preceding junction constraint Y and Z-direction translational degree of freedom；Left back junction constraint X and Z-direction translational degree of freedom；It is right
Junction constraint Y and Z-direction translational degree of freedom afterwards.Load setting are as follows: mono- using rigid at horizontal bar in the middle part of the Non-carrying type white body
Member concentrates load manner or so to carry out load 1000N.According to bending stiffness calculation formulaObtain maximum Z-direction displacement
For 0.572mm.Obtaining bending stiffness is 3500N/mm.
Torsion stiffness analysis finally is carried out to Non-carrying type white body.Boundary condition is set first.Constrained is front truck
Two installation points in body vehicle frame junction middle position and last vehicle frame vehicle body.The way of restraint are as follows: constraint foreside bodywork vehicle frame installation
Middle part Z is put to Pingdu freedom degree.Constrain rear portion vehicle body frames installation point six direction whole freedom degree.Load setting are as follows: preceding
It is 1000N that portion's vehicle body frames installation point left-right position, which loads opposite a pair of of the power size of the size same direction,.According to torsion stiffness
Calculation formulaWherein, GJ is body torsional rigdity；T is the twisting resistance being applied on vehicle body；L is vehicle body wheelbase；θ is
Vehicle body between centers torsion angle.Its calculation formula is:U1、U2The respectively Z-direction amount of deflection of left and right side girder.
Following table is part stringer deformation data.
| Serial number | ID number | Z-direction coordinate | ID number | Z-direction displacement |
| 1 | 1532987 | -1.45E-01 | 1532987 | -1.45E-01 |
| 2 | 1533030 | -1.93E-01 | 1533030 | -1.94E-01 |
| 3 | 1531784 | -2.48E-01 | 1531784 | -2.50E-01 |
| 4 | 1532485 | -3.20E-01 | 1532485 | -3.23E-01 |
| 5 | 1532569 | -4.33E-01 | 1532569 | -4.37E-01 |
| 6 | 1532643 | -5.56E-01 | 1532643 | -5.62E-01 |
| 7 | 1561353 | -6.50E-01 | 1561353 | -6.58E-01 |
| 8 | 153758 | -1.03E+00 | 153758 | -1.04E+00 |
| 9 | 3246599 | -1.38E+00 | 3246599 | -1.40E+00 |
| 10 | 1470930 | -2.03E+00 | 1470930 | -2.06E+00 |
Measuring left side power loading Position Z-direction deflection is that the right power loading Position Z-direction deflection of -4.945mm is
4.808mm.And two distances between load(ing) point is 1001.673mm.Can be calculated windup-degree is 0.557 °.According to torsion stiffness
Calculation formula obtains k=13157Nm/deg.
Step 3: bending stiffness, torsion stiffness, one order analysis are carried out.With the minimum target of white body gross mass,
It is constraint with bending stiffness and the displacement of torsion stiffness load loading Position.It is to ring with the displacement of vehicle frame measurement point and vehicle body gross mass
It answers.Non-carrying type white body Stiffness Sensitivity is carried out to calculate.Secondly the sensitivity of single order torsion mode and mass sensitivity meter are carried out
It calculates.Equally with the minimum target of total quality.It is response with mode and total quality.It is that constraint carries out spirit with single order torsion mode
Sensitivity calculates.Following table is sensitivity portions calculated result.
Step 4: by the calculated direct sensitivity of step 3 according to relative sensitivity calculation formula:
Calculate relative sensitivity.Finally select 8 groups of opposite maximum components of single order torsion mode sensitivity.Following table is to select
Unit number and position.
| Serial number | ID number | Position |
| 1 | I05801990190_0P8MM_HC220Y | Front bumper water tank frame part |
| 2 | I05801996552_0P8MM_DC04 | Along inner panel crossbeam under front windshield |
| 3 | I05801990248_0P8MM_HC180Y | Anticollision beam for front bumper |
| 4 | I05801994671_1P2MM_DC04 | Firewall frame |
| 5 | I05801994690_0P8MM_DC04 | Front firewall |
| 6 | I05801994754_0P8MM_DC04 | Left and right sides lateral coaming plate outside plate |
| 7 | I05801994617_1P2MM_DC03 | The big plate crossbeam in top |
| 8 | I05801994614_1P0MM_DC04 | Tail-gate frame outside plate |
Step 5: the multiple-objection optimization based on response surface model is carried out to the component selected, optimum results are as shown in the table.
| Serial number | ID number | Original depth | After optimization |
| 1 | I05801990190_0P8MM_HC220Y | 0.8mm | 0.7mm |
| 2 | I05801996552_0P8MM_DC04 | 0.8mm | 0.7mm |
| 3 | I05801990248_0P8MM_HC180Y | 0.8mm | 0.8mm |
| 4 | I05801994671_1P2MM_DC04 | 1.2mm | 1.0mm |
| 5 | I05801994690_0P8MM_DC04 | 0.8mm | 0.7mm |
| 6 | I05801994754_0P8MM_DC04 | 0.8mm | 0.8mm |
| 7 | I05801994617_1P2MM_DC03 | 1.2mm | 1.1mm |
| 8 | I05801994614_1P0MM_DC04 | 1.0mm | 0.8mm |
Step 6: by carry out it is dimensionally-optimised after component assign attribute again after, re-started according to the method for step 2 quiet
State rigidity and model analysis.Bending stiffness after optimization is that 3720N/mm is slightly improved, and torsion stiffness is obtained according to calculation formula
K=13200Nm/deg remains basically stable.Therefore lightweight concept feasible.
The aforementioned description to specific exemplary embodiment of the invention is in order to illustrate and illustration purpose.These descriptions
It is not wishing to limit the invention to disclosed precise forms, and it will be apparent that according to the above instruction, can much be changed
And variation.The purpose of selecting and describing the exemplary embodiment is that explaining specific principle of the invention and its actually answering
With so that those skilled in the art can be realized and utilize a variety of different exemplary implementation schemes of the invention and
Various chooses and changes.The scope of the present invention is intended to be limited by claims and its equivalents.
Claims (7)
1. a kind of Non-carrying type body in white light weight method based on relative sensitivity, it is characterised in that: in accordance with the following steps into
Row:
Step 1, according to CATIA three-dimension modeling finite element analysis model；
Step 2, Non-carrying type white body bending stiffness torsion stiffness and model analysis are carried out；
Step 3, rigidity and Modal sensitivity response analysis model are established respectively；
Step 4, Relative sensitivity analysis is carried out on the basis of sensitivity analysis and selects lightweight component；
Step 5, dimensionally-optimised to the component progress multiple target filtered out；
Step 6, the Non-carrying type white body after lightweight is subjected to performance verification.
2. the Non-carrying type body in white light weight method according to claim 1 based on relative sensitivity, which is characterized in that
Step 1 specifically:
1.1 need to meet according to CATIA three-dimension modeling finite element model, mesh quality: warp < 15 ° warpage or；
Skewness<60°；Jacobian≧0.6；Ratio of length to width≦5；Minimum internal angle
Of CQUAD4=45 °；Maxmum internal angle of CQUAD4=135 °；Minimum internal angle
Of CTRIA3=15 °；Maxmum internal angle of CTRIA3=105 °；
1.2 thin plate junction solder joint units use ace (general) type；Place is bolted using RBE3 unit；Vehicle frame vehicle body
Junction and suspension installation point use RIGID unit；
Bilayer washer unit is used around 1.3 bolts hole, plate sheet welding marginal portion mesh-density is bilayer；
1.4 assign different material properties to component according to part library table.
3. the Non-carrying type body in white light weight method according to claim 2 based on relative sensitivity, which is characterized in that
Step 2 specifically:
2.1 pairs of Non-carrying type white bodies carry out Free Modal Analysis, that is, boundary condition and load is not added；Its mathematical model are as follows:
Wherein K, C, M are the stiffness matrix, damping matrix and mass matrix of system respectively；X and F
It is the motion vector and excitation force vector of system respectively, respectively indicates are as follows:
X=[x1x2......xr......xN]Γ
F=[f1f2......fr......fN]Γ；
Two vectors are decoupled, need to carry out certain conversion in Uncoupled procedure；I.e. physical coordinates modal coordinate
It replaces, it is final to realize solution of equations coupling, obtain the mode and the vibration shape under each frequency；
2.2 pairs of Non-carrying type white bodies carry out Bending Stiffness Analysis, first setting boundary condition；Constrained is white body and vehicle
Two simulating wheel installation points of the simulating wheel point of frame front or so two and Rear frame vehicle body；The way of restraint are as follows: left front junction
Constrain Z-direction translational degree of freedom；Right preceding junction constraint Y and Z-direction translational degree of freedom；Left back junction constraint X and Z-direction translation are freely
Degree；Junction constraint Y and Z-direction translational degree of freedom behind the right side；Load setting are as follows: used at horizontal bar in the middle part of the Non-carrying type white body
Rigid unit concentrfated load mode or so is loaded；
2.3 pairs of Non-carrying type white bodies carry out torsion stiffness analysis, first setting boundary condition；Constrained is front of the car vehicle frame
Two installation points in junction middle position and last vehicle frame vehicle body；The way of restraint are as follows: Z in the middle part of constraint foreside bodywork vehicle frame installation point
To Pingdu freedom degree；Constrain rear portion vehicle body frames installation point six direction whole freedom degree；Load setting are as follows: in foreside bodywork vehicle
Frame installation point left-right position loads opposite a pair of of the torque of the size same direction.
4. the Non-carrying type body in white light weight method according to claim 1 based on relative sensitivity, which is characterized in that
In step 3, sensitivity analysis is carried out by design variable of panel thickness d；The citation form of sensitivity analysis are as follows:
Wherein, X is the vector of body structure design parameter composition at reference point；X is the variation of body structure design parameter, default
Value is the 1% of the difference of upper and lower limit；E is the vector with X with dimension；U is body structure performance parameter；The mathematics of Stiffness Sensitivity
Model is by Rigidity Calculation formula:
[K]n*n{u}n*l={ F }n*l,
Wherein, [K]n*nFor the overall stiffness of research object；{u}n*lFor the motion vector of analysis model；{F}n*lFor analysis model
External applied load vector；Above formula can obtain after seeking local derviation to design variable d, that is, thickness:
[K,d]n*n{μ}n*l+[K]n*n{u,d}n*l={ F,d}n*l={ 0 }n*l,
{μ, d}=- [K]n*n -1[K,d]n*n{μ}n*l,
Wherein, [K,d]n*n -1It is the corresponding expansion of each unit for the global stiffness matrix of analysis model overall stiffness inverse matrix structural model
Rank matrix is formed by stacking；
It, can be by a kind of substitution of measurement point being displaced as stiffness response in Stiffness Sensitivity calculating；It is arranged not in load
Under conditions of change, the variation of displacement is the variation of rigidity；
Modal sensitivity is determined by material properties and thickness, with the minimum target of white body quality；First-order flexure mode is greater than
Original value is constraint, is that response is analyzed with quality and modal frequency.
5. the Non-carrying type body in white light weight method according to claim 1 based on relative sensitivity, which is characterized in that
Step 4 specifically:
By step 3 calculate separately out about bending stiffness, torsion stiffness, single order torsion mode, quality sensitivity after according to phase
To sensitivity definition formula:
Wherein SwFor the direct sensitivity of quality, SB isDirect bending stiffness sensitivity, StFor direct torsion stiffness sensitivity, SfIt is straight
Connect Modal sensitivity.
6. the Non-carrying type body in white light weight method according to claim 1 based on relative sensitivity, which is characterized in that
Step 5 specifically: by step 4 gained relative sensitivity as a result, body stiffness and Modal Performances and body quality can be improved by selecting
The component not being significantly increased；Select optimal Latin hypercube method that the performance of design variable each in step 2 is carried out experimental design；
First-order kernel surface model is established after obtaining test sample point:
In formula, a is multinomial coefficient；xjFor design variable；Q is design variable number；
Then coefficient of multiple correlation R is utilized2Carry out the accuracy of auth response face fitting；Its is defined as:
R2=1-QC/QZ
In formula, QCFor residual deviation quadratic sum；QZFor sum of square of deviations；
Finally, single order torsion mode, bending stiffness, torsion stiffness are constraint with body quality minimum target；Using population
Algorithm carries out multiple-objection optimization, wherein the general type of particle swarm algorithm are as follows:
vid=w × vid+c1×rand()×(pid-xid)+c2×Rand()×(pgd-xid)
xid=xid+vid,
In formula, wherein w is inertia weight, c1And c2For aceleration pulse, rand () and Rand () are two and become in [0,1] range
The random value of change；First item formula is Inertia in first formula, and particle is made to have the tendency that expanded search space；Section 2 is
" cognition " item indicates thinking of the particle to improvement direction itself；Section 3 is " society " item, indicates interparticle optimal information
It is shared.
7. the Non-carrying type body in white light weight method according to claim 1 based on relative sensitivity, it is characterised in that:
Step 6 specifically: by carry out it is dimensionally-optimised after component assign attribute again after, re-start static state according to the method for step 2
Whether rigidity and model analysis, the white body performance after comparison is dimensionally-optimised decline.
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