CN104112050B - A kind of light vehicle Non-carrying type frame optimum structure design method - Google Patents
A kind of light vehicle Non-carrying type frame optimum structure design method Download PDFInfo
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Abstract
A kind of light vehicle Non-carrying type frame optimum structure design method, it includes establishing the original vehicle frame structure three-dimensional geometrical model of light vehicle using SolidWorks softwares, and exports into IGES document format datas, obtains body frame structure for automotive IGES models；Body frame structure for automotive IGES models are read in Hypermesh softwares, geometric manipulations are carried out using Hypermesh softwares and divide finite element grid, on the premise of longitudinal beam and attached holder structure form is not changed, the topological optimization of frame cross structure is carried out using the structure optimization function of Hypermesh softwares, realizes the position of beam structure and the optimization design of structure type.Its purpose is to provide one kind on the premise of body frame structure for automotive weight is not increased, improve bending stiffness, torsion stiffness and the body frame structure for automotive intrinsic frequency of light vehicle vehicle frame, so that it is guaranteed that vehicle frame has higher overall stiffness, the light vehicle Non-carrying type frame optimum structure design method of the reliability of vehicle, security, control stability and vibration characteristics is improved.
Description
Technical field
The present invention relates to a kind of light vehicle Non-carrying type frame optimum structure design method.
Background technology
Body frame structure for automotive is used to vehicle body, driver's cabin, suspension etc. connecting into an entirety, almost carries vehicle and uses process
In various load, it is main to include bending, reverse and shock loading etc., under the action of these load, body frame structure for automotive it is firm
Degree characteristic has the function that very important.Body frame structure for automotive rigidity is unreasonable, can directly affect the bearing function of vehicle frame, and vehicle frame is overall
Rigidity is low, and the integrated carrying ability for making vehicle frame is reduced, and the local stiffness of vehicle frame is low, can make vehicle frame local deformation increase, vehicle frame
Insufficient rigidity can cause malformation excessive, influence to be installed on the relative position of assembly on vehicle frame.Meanwhile vehicle frame insufficient rigidity is also
Frame weaving frequency can be caused low, at this time, flexural vibrations, the twisting vibration of vehicle frame totality can be produced after vehicle frame excitation vibrated
Or the complex vibration of various vibrations, when driving frequency coincide with body frame structure for automotive intrinsic frequency or is close, easily tie vehicle frame
Structure resonates, final ride performance, comfort and maneuverability for directly or indirectly influencing vehicle etc..
When carrying out the design of light vehicle body frame structure for automotive, traditional way is improved on the basis of original structure scheme
Design, the reasonability for the method test design then examined again by real steering vectors, if improved design project can not meet to want
Ask, need to be designed with re-starting.This method cycle length, it is costly, design requirement is unable to reach sometimes.Optimal Structure Designing side
Method, such as：Structural Shape Optimization, it is dimensionally-optimised body frame structure for automotive design in also applied, but be only limitted to carry out structure partial
Improvement or structure size change, without being changed to the overall topology of body frame structure for automotive.
Structural Topology Optimization Design method is mainly used for the schematic design phase of structure, by the transmission for calculating structural loads
Path, determines optimal distribution of the structural material in space, and the structure distribution form provided often has with traditional structure arrangement form
Very big difference.For light vehicle body frame structure for automotive, the Curve guide impeller of structure is carried out or using shape according to conventional method
The optimum structure design method such as optimization, dimensionally-optimised can only bend the totality of structure, torsion stiffness carries out local adjustment.
The crossbeam that the original body frame structure for automotive of light vehicle mainly adds some parallel arrangements by the two big longeron in both sides forms,
In order to improve the overall structure rigidity of body frame structure for automotive, using the design method of structural Topology Optimization, to body frame structure for automotive header portion
Structural topology form optimize, for improve body frame structure for automotive bending, torsion stiffness and structural natural frequencies, and
And then improve the system performance for improving vehicle indirectly and all have great importance.
The content of the invention
It is an object of the invention to provide one kind on the premise of body frame structure for automotive weight is not increased, light vehicle vehicle frame is improved
Bending stiffness, torsion stiffness and body frame structure for automotive intrinsic frequency, so that it is guaranteed that vehicle frame has a higher overall stiffness, improve car
Reliability, security, the light vehicle Non-carrying type frame Optimal Structure Designing side of control stability and vibration characteristics
Method.
A kind of light vehicle Non-carrying type frame optimum structure design method of the present invention, includes the following steps：
(1) the original vehicle frame structure three-dimensional geometrical model of light vehicle is established using SolidWorks softwares, and export into
IGES document format datas, obtain body frame structure for automotive IGES models；
(2) body frame structure for automotive IGES models are read in Hypermesh softwares, several where carried out using Hypermesh softwares
Manage and divide finite element grid, in Optimal Structure Designing, do not change the structure type of the attached seat of vehicle frame, therefore several where carried out
When reason and finite element modeling, the finite element model of body frame structure for automotive longeron and beam structure is only established, since frame cross being made
For the design section of structure optimization, the finite element model of longitudinal beam is established using two-dimentional shell unit, using three-dimensional hexahedron net
The design section that lattice filling frame cross may be distributed, is connected two-dimensional cell and three-dimensional element by the way of node connection
Connect, complete body frame structure for automotive finite element modeling；
(3) Frame Load and boundary condition loading：Body frame structure for automotive is primarily subjected to bending and torsional load, establishes vehicle frame respectively
Bending and torsional load operating mode.The bending load operating mode mainly examines the bending stiffness of body frame structure for automotive, under the operating mode, constraint
Vehicle frame fixes all frees degree of supporting point with fore suspension and rear suspension, and in central frame beam position, the equivalent railway carriage that loads is from heavy load and cargo
Loading capacity；The torsional load mainly examines the torsion stiffness of body frame structure for automotive, when loading body frame structure for automotive torsional load, constrains car
Frame and rear suspension fix all frees degree of supporting point, then vehicle frame and front suspension fix at supporting point apply it is equal in magnitude,
The opposite vertical direction concentrfated load in direction；
(4) design section and design variable definition：The distributed areas of body frame structure for automotive crossbeam are defined as design section, by three
The relative density of dimension hexahedral element is defined as design variable, in process of optimization, according to the size of unit relative density, certainly
Determine whether to accept or reject the unit in structure, according to construction weight index and stiffness requirement, take the unit relative density threshold value to be
0.285, give up the construction unit that unit relative density is less than threshold value；
(5) objective function：When carrying out body frame structure for automotive optimization design to improve the bending of body frame structure for automotive to greatest extent
6 rank natural frequency values are target before rigidity, torsion stiffness and body frame structure for automotive；Defined in Hypermesh software optimization modules
Weighted target functionK is object function, k1、k2Respectively bending stiffness and torsion stiffness, w1、w2
Respectively correspond to the weighting coefficient of bending stiffness and torsion stiffness, wjCorresponding to the weighting coefficient of 6 rank intrinsic frequencies before vehicle frame,
λj6 rank natural frequency value, w before body frame structure for automotiveoFor for balancing bending, torsional load operating mode and the weighting system of structural natural frequencies
Number, since the order of magnitude of bend stiffness is 106, the order of magnitude of torsion stiffness value is 102, and 6 rank natural frequency values before structure
The order of magnitude is also 102, therefore take w1=1, w2=3.25 × 104、wj=1, w0=2.18 × 104；
(6) made in Hypermesh software optimization modules weighted target function K maximize, using topological optimization function into
Driving frame Structural Topology Optimization Design, obtaining body frame structure for automotive crossbeam, the body frame structure for automotive of distributing position and distribution form is opened up in space
Flutter density cloud atlas；
(7) body frame structure for automotive geometrical model and finite element model are reconstructed according to body frame structure for automotive topology density cloud atlas, obtained excellent
Light vehicle Non-carrying type frame structure after change.
A kind of light vehicle Non-carrying type frame optimum structure design method of the present invention, using the side of Optimal Structure Designing
Method, gives light vehicle body frame structure for automotive optimization design step, it is contemplated that the bending born during body frame structure for automotive use carries
The influence of lotus, torsional load and oscillating load, establishes the Optimized model of light vehicle Non-carrying type frame structure, into driving frame
The topology optimization design of beam structure, and then obtain a kind of frame cross new structural form rearranged.Under same load,
From the point of view of the performance comparison for optimizing structure and prototype structure, body frame structure for automotive weight do not have it is increased under the premise of, structure after optimization
Bending stiffness improves 15% than prototype structure, and torsion stiffness improves 24%, and the preceding 6 rank intrinsic frequency of body frame structure for automotive averagely carries
It is high by 5%, good optimization design effect is played, the design side of science is provided for the optimization of same type body frame structure for automotive
Method.The present invention adds the structure shape of some parallel arrangement crossbeams for existing light vehicle body frame structure for automotive using two big longeron
Formula, using Structural Topology Optimization Design method, on the basis of body frame structure for automotive finite element model is established, to the header portion of vehicle frame into
Row redesigns, and changes the structural arrangement form of crossbeam, to ensure on the premise of body frame structure for automotive weight is not increased, improves light-duty
Bending stiffness, torsion stiffness and the body frame structure for automotive intrinsic frequency of carriage frame, so that it is guaranteed that vehicle frame has had higher entirety just
Degree, improves reliability, security, control stability and the vibration characteristics of vehicle.
The present invention is described in detail with reference to the accompanying drawings and embodiments.
Brief description of the drawings
Fig. 1 is original light vehicle body frame structure for automotive geometrical model；
Fig. 2 is the load condition of bending load operating mode vehicle frame；
Fig. 3 is the load condition of torsional load operating mode vehicle frame；
Fig. 4 is body frame structure for automotive original design space of the present invention；
Fig. 5 A are body frame structure for automotive topological optimization density cloud atlas of the present invention；
Fig. 5 B are body frame structure for automotive topological optimization density contour surface figure of the present invention；
Fig. 6 is that the vehicle frame that the present invention is obtained according to topological optimization density cloud atlas optimizes CAD model figure；
Fig. 7 is final optimization pass Rear frame general structure schematic diagram of the present invention, without attached seating portion.
In Fig. 1：1. longitudinal beam, 2. frame cross, attached seat before 3. driver's cabins, the 4. attached seats in front suspension side, 5. driver's cabins
Attached seat afterwards, attached seat before 6. railway carriages, attached seat after 7. railway carriages, attached seat before 8. rear suspensions, attached seat after 9. rear suspensions；In Fig. 4：Dark portion
Divide and represent Non-design region, light-colored part represents topology optimization design region；
In the figure 7：1. vehicle frame right-hand stringer, 2. vehicle frame transom beams, 3. vehicle frame tail K shape crossbeams, 4. vehicle frame left-hand stringers, 5.
Vehicle frame head X-shaped cross members, 6. vehicle frame head crossbeams.
Embodiment
The invention discloses a kind of optimum design method of light vehicle Non-carrying type frame structure, which mainly includes
Body frame structure for automotive geometrical model is established, body frame structure for automotive simplification Equivalent finite element model, loading Frame Load and boundary condition is established, is fixed
Adopted optimization design region and design variable, define optimization object function, Structural Topology Optimization Design, body frame structure for automotive geometrical model weight
The implementation steps such as structure and structure verification.
A kind of light vehicle Non-carrying type frame optimum structure design method of the present invention, includes the following steps：
(1) the original vehicle frame structure three-dimensional geometrical model of light vehicle is established using SolidWorks softwares, and export into
IGES document format datas, obtain body frame structure for automotive IGES models；
(2) body frame structure for automotive IGES models are read in Hypermesh softwares, several where carried out using Hypermesh softwares
Manage and divide finite element grid, in Optimal Structure Designing, do not change the structure type of the attached seat of vehicle frame, therefore several where carried out
When reason and finite element modeling, the finite element model of body frame structure for automotive longeron and beam structure is only established, since frame cross being made
For the design section of structure optimization, the finite element model of longitudinal beam is established using two-dimentional shell unit, using three-dimensional hexahedron net
The design section that lattice filling frame cross may be distributed, is connected two-dimensional cell and three-dimensional element by the way of node connection
Connect, complete body frame structure for automotive finite element modeling；
(3) Frame Load and boundary condition loading：Body frame structure for automotive is primarily subjected to bending and torsional load, establishes vehicle frame respectively
Bending and torsional load operating mode.The bending load operating mode mainly examines the bending stiffness of body frame structure for automotive, under the operating mode, constraint
Vehicle frame fixes all frees degree of supporting point with fore suspension and rear suspension, and in central frame beam position, the equivalent railway carriage that loads is from heavy load and cargo
Loading capacity；The torsional load mainly examines the torsion stiffness of body frame structure for automotive, when loading body frame structure for automotive torsional load, constrains car
Frame and rear suspension fix all frees degree of supporting point, then vehicle frame and front suspension fix at supporting point apply it is equal in magnitude,
The opposite vertical direction concentrfated load in direction；
(4) design section and design variable definition：The distributed areas of body frame structure for automotive crossbeam are defined as design section, by three
The relative density of dimension hexahedral element is defined as design variable, in process of optimization, according to the size of unit relative density, certainly
Determine whether to accept or reject the unit in structure, according to construction weight index and stiffness requirement, take the unit relative density threshold value to be
0.285, give up the construction unit that unit relative density is less than threshold value；
(5) objective function：When carrying out body frame structure for automotive optimization design to improve the bending of body frame structure for automotive to greatest extent
6 rank natural frequency values are target before rigidity, torsion stiffness and body frame structure for automotive；Defined in Hypermesh software optimization modules
Weighted target functionK is object function, k1、k2Respectively bending stiffness and torsion stiffness, w1、w2
Respectively correspond to the weighting coefficient of bending stiffness and torsion stiffness, wjCorresponding to the weighting coefficient of 6 rank intrinsic frequencies before vehicle frame,
λj6 rank natural frequency value, w before body frame structure for automotiveoFor for balancing bending, torsional load operating mode and the weighting system of structural natural frequencies
Number, since the order of magnitude of bend stiffness is 106, the order of magnitude of torsion stiffness value is 102, and 6 rank natural frequency values before structure
The order of magnitude is also 102, therefore take w1=1, w2=3.25 × 104、wj=1, w0=2.18 × 104；
(6) made in Hypermesh software optimization modules weighted target function K maximize, using topological optimization function into
Driving frame Structural Topology Optimization Design, obtaining body frame structure for automotive crossbeam, the body frame structure for automotive of distributing position and distribution form is opened up in space
Flutter density cloud atlas；
(7) body frame structure for automotive geometrical model and finite element model are reconstructed according to body frame structure for automotive topology density cloud atlas, obtained excellent
Light vehicle Non-carrying type frame structure after change.
A kind of specific implementation process of the optimum design method of light vehicle Non-carrying type frame structure of the present invention is specific
Comprise the following steps：
1) light vehicle vehicle frame prototype structure 3-D geometric model is established using SolidWorks softwares, as shown in Figure 1, former
Beginning body frame structure for automotive mainly by attached seat 5 after attached seat 3, the attached seat 4 in front suspension side, driver's cabin before two longerons 1,9 crossbeam 2, driver's cabin,
Attached seat 9 etc. forms after attached seat 8, rear suspension before attached seat 7, rear suspension after attached seat 6, railway carriage before railway carriage.And export into IGES data text
Part form, obtains body frame structure for automotive IGES models.
2) body frame structure for automotive finite element modeling.Body frame structure for automotive IGES models are read in Hypermesh softwares, several where carried out
Manage and divide finite element grid, in Optimal Structure Designing, do not change the structure type of the attached seat of vehicle frame, therefore several where carried out
When reason and finite element modeling, the finite element model of body frame structure for automotive longeron and beam structure is only established, since frame cross being made
For the design section of structure optimization, the finite element model of longitudinal beam is established using two-dimentional shell unit, using three-dimensional hexahedron net
The design section that lattice filling frame cross may be distributed, is connected two-dimensional cell and three-dimensional element by the way of node connection
Connect, complete body frame structure for automotive finite element modeling.
3) Frame Load and boundary condition loading.Consider during Optimal Structure Designing vehicle frame bending load, torsional load,
And 3 kinds of operating modes such as structural natural frequencies.The bending load operating mode mainly considers light weight and bearing load to vehicle frame knot
The influence of structure deformation, under bending load operating mode the load condition of vehicle frame as shown in Fig. 2, under the operating mode, constraint vehicle frame with it is front and rear
Suspension fixes all frees degree of supporting point, and in central frame beam position, the equivalent railway carriage that loads is from heavy load and DWCC dead weight cargo capacity.Institute
State the torsion stiffness that torsional load is mainly used for examining body frame structure for automotive, load condition such as Fig. 3 institutes of vehicle frame under torsional load operating mode
Show, when loading body frame structure for automotive torsional load, constraint vehicle frame fixes all frees degree of supporting point with rear suspension, then in vehicle frame
Fixed with front suspension and apply vertical direction concentrfated load equal in magnitude, direction is opposite at supporting point.
4) design section and design variable definition.The distributed areas of body frame structure for automotive crossbeam are defined as design section, by three
The density of dimension hexahedral element is defined as design variable, in process of optimization, according to the size of unit relative density, determines knot
Whether the unit is accepted or rejected in structure, and according to construction weight index and stiffness requirement, it is 0.285 to take unit relative density threshold value, house
Abandon the construction unit that unit relative density is less than threshold value.Determine body frame structure for automotive original design space as shown in Figure 4, wherein vehicle frame is indulged
Beam is Non-design region, is represented in figure with dark parts；Frame cross position is design section, and light-colored part table is used in figure
Show.
5) objective function.With 6 rank intrinsic frequencies before the bending stiffness, torsion stiffness and body frame structure for automotive of body frame structure for automotive
Maximum turns to target, builds weighted target functionK is object function, k1、k2Respectively bending is firm
Degree and torsion stiffness, w1、w2Respectively correspond to the weighting coefficient of bending stiffness and torsion stiffness, wjConsolidate corresponding to 6 ranks before vehicle frame
There are the weighting coefficient of frequency, λj6 rank natural frequency value, w before body frame structure for automotiveoFor for balancing bending, torsional load operating mode and structure
The weighting coefficient of intrinsic frequency, since the order of magnitude of bend stiffness is 106, the order of magnitude of torsion stiffness value is 102, and structure
The order of magnitude of preceding 6 rank natural frequency value is also 102, therefore take w1=1, w2=3.25 × 104、wj=1, w0=2.18 × 104；
6) make weighted target function K maximize in Hypermesh software optimization modules, carried out using topological optimization function
Body frame structure for automotive topology optimization design, obtains body frame structure for automotive crossbeam distributing position and the distribution in space as shown in Fig. 5 A, Fig. 5 B
The topological density cloud atlas of form.
7) the body frame structure for automotive topological optimization shown in the body frame structure for automotive topological optimization density cloud atlas and Fig. 5 B according to Fig. 5 A
Density contour surface figure, reconstructs body frame structure for automotive CAD model figure as shown in Figure 6, finite element modeling is re-started, so as to be optimized
Light vehicle Non-carrying type frame structure afterwards, its structure diagram are as shown in Figure 7.
Claims (1)
1. a kind of light vehicle Non-carrying type frame optimum structure design method, it is characterised in that include the following steps：
(1) the original vehicle frame structure three-dimensional geometrical model of light vehicle is established using SolidWorks softwares, original body frame structure for automotive by
Before two longerons (1), 9 crossbeams (2), driver's cabins after attached seat (3), the attached seat in front suspension side (4), driver's cabin before attached seat (5), railway carriage
Attached seat (9) forms after attached seat (8), rear suspension before attached seat (7), rear suspension after attached seat (6), railway carriage, and exports into IGES data text
Part form, obtains body frame structure for automotive IGES models；
(2) body frame structure for automotive IGES models are read in Hypermesh softwares, geometric manipulations are carried out simultaneously using Hypermesh softwares
Divide finite element grid, in Optimal Structure Designing, do not change the structure type of the attached seat of vehicle frame, thus carry out geometric manipulations and
During finite element modeling, the finite element model of body frame structure for automotive longeron and beam structure is only established, due to using frame cross as knot
The design section of structure optimization, the finite element model of longitudinal beam is established using two-dimentional shell unit, is filled out using three-dimensional hexahedral mesh
The design section that frame cross may be distributed is filled, is attached two-dimensional cell and three-dimensional element by the way of node connection,
Complete body frame structure for automotive finite element modeling；
(3) Frame Load and boundary condition loading：Body frame structure for automotive is primarily subjected to bending and torsional load, establishes vehicle frame bending respectively
And torsional load operating mode；The bending load operating mode mainly examines the bending stiffness of body frame structure for automotive, under the operating mode, constrains vehicle frame
All frees degree of supporting point are fixed with fore suspension and rear suspension, the equivalent railway carriage that loads is from heavy load and cargo load-carrying in central frame beam position
Amount；The torsional load mainly examines the torsion stiffness of body frame structure for automotive, when loading body frame structure for automotive torsional load, constraint vehicle frame with
Rear suspension fixes all frees degree of supporting point, is then fixed in vehicle frame and front suspension and applies equal in magnitude, direction at supporting point
Opposite vertical direction concentrfated load；
(4) design section and design variable definition：The distributed areas of body frame structure for automotive crossbeam are defined as design section, by three-dimensional six
The relative density of face body unit is defined as design variable, in process of optimization, according to the size of unit relative density, determines knot
Whether the unit is accepted or rejected in structure, and according to construction weight index and stiffness requirement, it is 0.285 to take unit relative density threshold value, house
Abandon the construction unit that unit relative density is less than threshold value；
(5) objective function：When carrying out body frame structure for automotive optimization design with improve to greatest extent the bending stiffness of body frame structure for automotive,
6 rank natural frequency values are target before torsion stiffness and body frame structure for automotive；Mesh is weighted defined in Hypermesh software optimization modules
Scalar functionsK is object function, k1、k2Respectively bending stiffness and torsion stiffness, w1、w2Respectively
Corresponding to the weighting coefficient of bending stiffness and torsion stiffness, wjCorresponding to the weighting coefficient of 6 rank intrinsic frequencies before vehicle frame, λjVehicle frame
6 rank natural frequency value, w before structureoFor for balance bending, torsional load operating mode and structural natural frequencies weighting coefficient, by
In bend stiffness the order of magnitude be 106, the order of magnitude of torsion stiffness value is 102, and before structure 6 rank natural frequency values quantity
Level is also 102, therefore take w1=1, w2=3.25 × 104、wj=1, w0=2.18 × 104；
(6) weighted target function K is made to maximize in Hypermesh software optimization modules, using topological optimization function into driving
Frame Structural Topology Optimization Design, obtaining body frame structure for automotive crossbeam, the body frame structure for automotive topology of distributing position and distribution form is close in space
Spend cloud atlas；
(7) body frame structure for automotive geometrical model and finite element model are reconstructed according to body frame structure for automotive topology density cloud atlas, after obtaining optimization
Light vehicle Non-carrying type frame structure.
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