CN103345550A - Weight-reduction optimization method for automobile instrument board beam - Google Patents
Weight-reduction optimization method for automobile instrument board beam Download PDFInfo
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- CN103345550A CN103345550A CN201310268121XA CN201310268121A CN103345550A CN 103345550 A CN103345550 A CN 103345550A CN 201310268121X A CN201310268121X A CN 201310268121XA CN 201310268121 A CN201310268121 A CN 201310268121A CN 103345550 A CN103345550 A CN 103345550A
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Abstract
The invention discloses a weight-reduction optimization method for an automobile instrument board beam. Through instrument board beams of existing reference automobile models, CAE is carried out to analyze models and calculate modality factor delta values of parts, the parts are classified according to the delta values, then different weight-reduction optimization methods are used for parts of different types, and finally the MCS NASTRAN software is used for analysis validation on the optimized model, and therefore a lightweight design of the automobile instrument board beam is achieved. By means of the method, design staff can conveniently carry out the optimization design on the automobile instrument board beam, design efficiency is improved, and design cost is lowered.
Description
Technical field
The present invention relates to a kind of loss of weight optimization method of fascia crossbeam.
Background technology
The lightweight of automobile reduces discharging and plays crucial effects for reducing oil consumption, has become the research focus of domestic and international auto industry circle at present.Guaranteeing each assembly parts of optimal design on the basis of original performance, continuing to optimize the vehicle spectrum is the light-weighted dominant ideas of automobile.Fascia crossbeam (being called for short CCB) assembly is the automobile dashboard system inner skeleton, play support meter plate system, the installation of parts in the instrument panel syste being provided, the intensity that increases whole vehicle body is also had certain effect, is instrument panel syste and the support that is connected of body in white assembly.The present invention has introduced a kind of Optimization Design of dashboard cross member, alleviates the weight of dashboard cross member assembly, has reached the light-weighted target of automobile.
Traditional fascia beam design is in order to satisfy its performance requirement, part is strengthened simply, and traditional method for designing is time-consuming but also poor efficiency not only, and has following problem:
(1) all parts is strengthened not having specific aim and directivity;
(2) all parts are strengthened or are weakened the irrational utilization that has caused material.
Summary of the invention
Purpose of the present invention, a kind of Optimization Design of fascia crossbeam is provided in order to address the above problem exactly, can rapidly and efficiently be optimized design to the fascia crossbeam based on original design parameter, thereby reach the loss of weight optimization of fascia crossbeam.
The object of the present invention is achieved like this:
The loss of weight optimization method of a kind of fascia crossbeam of the present invention may further comprise the steps:
The first step: the reference data of reading in the fascia crossbeam before optimizing;
Second step: to the dashboard cross member before optimizing carry out model analysis, the quiet stiffness analysis of support, crash analysis draw the fascia crossbeam before optimizing the whole model frequency of single order, each support quiet rigidity value and draw out impact curve, as the reference performance index of estimating the fascia crossbeam after optimizing;
The 3rd step: carry out the mode factor delta value that the cae analysis model calculates each parts that constitutes the fascia crossbeam by the reference data of the fascia crossbeam before optimizing;
The 4th step: the size according to mode factor delta value is carried out category division to each part that constitutes the fascia crossbeam;
The 5th step: different classes of part is carried out loss of weight optimization by CATIA software;
The 6th step: by MSC NASTRAN software the fascia crossbeam after optimizing is carried out analysis verification, quiet rigidity value and the impact curve of the whole model frequency of the single order of the fascia crossbeam after optimizing, each part mounting points are compared with the reference performance index before the optimization;
If the reference performance index before the whole model frequency of the single order of the fascia crossbeam after optimizing is optimized is compared, its variable quantity descends 5% with interior or raising, the quiet rigidity value of part mounting points is less than 1mm, or the quiet rigidity value of part mounting points during greater than 1mm with optimize before the reference performance index compare, its variable quantity descends in 5%, and the impact curve movement tendency before optimizing the back and optimizing is identical, then reaches designing requirement;
Otherwise, continued to carry out the 5th step.
The loss of weight optimization method of above-mentioned a kind of fascia crossbeam, wherein, in described the 4th step, the classification of part is divided into frame member and non-frame member, frame member refers to mode factor delta value greater than 0.5 part, and non-frame member refers to that mode factor delta value is less than or equal to 0.5 part.
The loss of weight optimization method of above-mentioned a kind of fascia crossbeam, wherein, in described the 5th step, loss of weight optimization mainly is optimized from part thickness and geometry thereof, need pay close attention to the variation of the quiet rigidity of mode and mounting points when wherein the loss of weight of frame member being optimized simultaneously; When being optimized, non-frame member need pay close attention to the variation of the quiet rigidity of mounting points.
The present invention can make things convenient for the designer for the optimal design of fascia crossbeam by above-mentioned steps greatly, improves the efficient of design, reduces design cost.
Description of drawings
Fig. 1 is that the dashboard cross member that reads in original vehicle is analyzed schematic diagram data;
Fig. 2 is the mode factor delta value synoptic diagram of each part on the fascia crossbeam of the present invention;
Fig. 3 is each part classification synoptic diagram on the fascia crossbeam of the present invention;
Fig. 4 optimizes front and back structure contrast synoptic diagram for fascia crossbeam of the present invention;
Fig. 5 optimizes the whole model frequency contrast of front and back single order synoptic diagram for fascia crossbeam of the present invention;
Fig. 6 optimizes the contrast synoptic diagram of the quiet rigidity value of each part mounting points of front and back for fascia crossbeam of the present invention;
Fig. 7 optimizes front and back CCB collision checking---FEA side impact impact curve contrast synoptic diagram for fascia crossbeam of the present invention;
Fig. 8 optimizes front and back CCB collision checking for fascia crossbeam of the present invention---bump impact curve contrast synoptic diagram before the FEA.
Embodiment
Below in conjunction with accompanying drawing, the invention will be further described.
The invention discloses a kind of Optimization Design of body of a motor car, comprise the steps:
The first step: read in the reference data of the fascia crossbeam before optimizing, as shown in Figure 1, the dashboard cross member that for example reads in original vehicle is analyzed data;
Second step: to the dashboard cross member before optimizing carry out model analysis, the quiet stiffness analysis of support, crash analysis draw the fascia crossbeam before optimizing the whole model frequency of single order, mounting points quiet rigidity value and draw out impact curve figure, as the performance index of estimating the fascia crossbeam after optimizing;
The 3rd step: carry out the mode factor delta value that the cae analysis model calculates each parts that constitutes the fascia crossbeam by the reference data of the fascia crossbeam before optimizing, in dashboard cross member reference data shown in Figure 1, the mode factor delta value of each part as shown in Figure 2;
The 4th step: according to the size of mode factor delta value each part that constitutes the fascia crossbeam being carried out category division is frame member and non-member, frame member is mode factor delta value greater than 0.5 part, non-frame member refers to that mode factor delta value is less than or equal to 0.5 part, in dashboard cross member reference data shown in Figure 1, represent frame member as black part among Fig. 3, white part is represented non-frame member;
The 5th step: use different optimal design modes to be optimized to different classes of part by CATIA software, can strengthen the bigger part of the mode factor (can increase part thickness and its planform is increased some flange or reinforcement comes its reinforcement) when optimizing at frame member, weaken the less part of the mode factor (can reduce part thickness and to its planform simplification etc.), not only need to pay close attention to the rigidity value that each part is paid close attention to mounting points to influence but also the needs of mode during optimization; Can be earlier to the part thickness attenuate when optimizing at non-frame member, then it is increased some flange to its planform or reinforcement comes it is strengthened, but need to pay close attention to the quiet rigidity value of each part, its overall contrast structure is as shown in Figure 4;
The 6th step: the fascia crossbeam after optimizing is carried out analysis verification by MSC NASTRAN software, quiet rigidity value and the impact curve of the whole model frequency of the single order of the fascia crossbeam after optimizing, each part mounting points are compared with the reference performance index before the optimization, and wherein quiet rigidity value is chosen the 50N deflection and is characterized:
The single order integral body model frequency reference performance index preceding than optimization as if the fascia crossbeam after optimizing compared, and its variable quantity descends 5% with interior or raising (Fig. 5 shows fascia crossbeam optimization front and back single order integral body model frequency contrast synoptic diagram);
The 50N deflection of part mounting points is less than 1mm, or when the 50N of part mounting points deflection during greater than 1mm, compare with the reference performance index before optimizing, its variable quantity descends 5% with interior (Fig. 6 shows quiet rigidity value (50N deflection) the contrast synoptic diagram that the fascia crossbeam is optimized each support of front and back); And,
Impact curve movement tendency before optimizing the back and optimizing identical (Fig. 7 and Fig. 8 show the fascia crossbeam optimize before and after CCB collision checking---the FEA side impact and before bump impact curve and contrast synoptic diagram), then reach designing requirement;
Otherwise, continued to carry out the 5th step.
The present invention can reach the purpose that alleviates fascia crossbeam weight by above-mentioned steps, simultaneously, has also saved material, has improved stock utilization, has saved cost, meets the light-weighted requirement of current social automobile.
Above embodiment is only for the usefulness that the present invention is described, but not limitation of the present invention, person skilled in the relevant technique, under the situation that does not break away from the spirit and scope of the present invention, can also make various conversion or modification, therefore all technical schemes that are equal to also should belong to category of the present invention, should be limited by each claim.
Claims (3)
1. the loss of weight optimization method of a fascia crossbeam is characterized in that, may further comprise the steps:
The first step: the reference data of reading in the fascia crossbeam before optimizing;
Second step: to the dashboard cross member before optimizing carry out model analysis, the quiet stiffness analysis of support, crash analysis draw the fascia crossbeam before optimizing the whole model frequency of single order, each support quiet rigidity value and draw out impact curve, as the reference performance index of estimating the fascia crossbeam after optimizing;
The 3rd step: carry out the mode factor delta value that the cae analysis model calculates each parts that constitutes the fascia crossbeam by the reference data of the fascia crossbeam before optimizing;
The 4th step: the size according to mode factor delta value is carried out category division to each part that constitutes the fascia crossbeam;
The 5th step: different classes of part is carried out loss of weight optimization by CATIA software;
The 6th step: by MSC NASTRAN software the fascia crossbeam after optimizing is carried out analysis verification, quiet rigidity value and the impact curve of the whole model frequency of the single order of the fascia crossbeam after optimizing, each part mounting points are compared with the reference performance index before the optimization;
If the reference performance index before the whole model frequency of the single order of the fascia crossbeam after optimizing is optimized is compared, its variable quantity descends 5% with interior or raising, the quiet rigidity value of part mounting points is less than 1mm, or the quiet rigidity value of part mounting points during greater than 1mm with optimize before the reference performance index compare, its variable quantity descends in 5%, and the impact curve movement tendency before optimizing the back and optimizing is identical, then reaches designing requirement;
Otherwise, continued to carry out the 5th step.
2. the loss of weight optimization method of a kind of fascia crossbeam as claimed in claim 1, it is characterized in that, in described the 4th step, the classification of part is divided into frame member and non-frame member, frame member refers to mode factor delta value greater than 0.5 part, and non-frame member refers to that mode factor delta value is less than or equal to 0.5 part.
3. the loss of weight optimization method of a kind of fascia crossbeam as claimed in claim 2, it is characterized in that, in described the 5th step, loss of weight optimization mainly is optimized from part thickness and geometry thereof, need pay close attention to the variation of the quiet rigidity of mode and mounting points when wherein the loss of weight of frame member being optimized simultaneously; When being optimized, non-frame member need pay close attention to the variation of the quiet rigidity of mounting points.
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103569213A (en) * | 2013-10-31 | 2014-02-12 | 富卓汽车内饰（安徽）有限公司 | Automobile instrument board cross beam assembly |
| CN106934117A (en) * | 2017-02-22 | 2017-07-07 | 江铃汽车股份有限公司 | Automobile instrument panel assembly optimization method |
| CN109710957A (en) * | 2017-10-26 | 2019-05-03 | 北京长城华冠汽车科技股份有限公司 | The hinged stiffness optimization method and system of multi link |
| CN111222263A (en) * | 2019-10-31 | 2020-06-02 | 长春英利汽车工业股份有限公司 | Finite element simulation method for instrument board beam vibration test |
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| CN101114311A (en) * | 2007-08-30 | 2008-01-30 | 上海交通大学 | Method for synthesizing finite element model in vehicle safety cooperative design |
| US20080127029A1 (en) * | 2006-10-31 | 2008-05-29 | International Business Machines Corporation | Closed-loop design for manufacturability process |
| CN102945307A (en) * | 2012-11-27 | 2013-02-27 | 北京汽车股份有限公司 | Automobile chassis key structural member structure optimization design method |
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Patent Citations (3)
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| US20080127029A1 (en) * | 2006-10-31 | 2008-05-29 | International Business Machines Corporation | Closed-loop design for manufacturability process |
| CN101114311A (en) * | 2007-08-30 | 2008-01-30 | 上海交通大学 | Method for synthesizing finite element model in vehicle safety cooperative design |
| CN102945307A (en) * | 2012-11-27 | 2013-02-27 | 北京汽车股份有限公司 | Automobile chassis key structural member structure optimization design method |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103569213A (en) * | 2013-10-31 | 2014-02-12 | 富卓汽车内饰（安徽）有限公司 | Automobile instrument board cross beam assembly |
| CN106934117A (en) * | 2017-02-22 | 2017-07-07 | 江铃汽车股份有限公司 | Automobile instrument panel assembly optimization method |
| CN109710957A (en) * | 2017-10-26 | 2019-05-03 | 北京长城华冠汽车科技股份有限公司 | The hinged stiffness optimization method and system of multi link |
| CN109710957B (en) * | 2017-10-26 | 2023-11-24 | 北京长城华冠汽车科技股份有限公司 | Multi-connecting-rod hinge stiffness optimization method and system |
| CN111222263A (en) * | 2019-10-31 | 2020-06-02 | 长春英利汽车工业股份有限公司 | Finite element simulation method for instrument board beam vibration test |
| CN111222263B (en) * | 2019-10-31 | 2023-04-07 | 长春英利汽车工业股份有限公司 | Finite element simulation method for instrument board beam vibration test |
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