CN104573246A - Front impact conceptual model design method for front structure of automobile - Google Patents
Front impact conceptual model design method for front structure of automobile Download PDFInfo
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- CN104573246A CN104573246A CN201510021926.3A CN201510021926A CN104573246A CN 104573246 A CN104573246 A CN 104573246A CN 201510021926 A CN201510021926 A CN 201510021926A CN 104573246 A CN104573246 A CN 104573246A
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Abstract
The invention discloses a front impact conceptual model design method for a front structure of an automobile. The front impact conceptual model design method for the front structure of the automobile includes that simplifying the front impact concept design for the automobile through building a lumped parameter model for the front of the automobile, and evaluating the impact resistance of the automobile at the concept design stage to regulate the axial impact resistance rigidity distribution of the automobile body and reinforce the impact resistance; building a multi-degree of freedom LPM consistent with the finished automobile structure at the concept design stage, and assigning a piecewise linear power-displacement relationship and a nonlinear moment-rotation curve to a corresponding spring unit in the LPM to define the axial impact rigidity and bending characteristics of the LPM. The front impact conceptual model design method for the front structure of the automobile simultaneously generates axial crushing and plastic bending deformation, realizes full automation, is capable of well meeting the demands on the impact resistance analysis for the automobile body in the automobile concept design stage, assists a designer in quickly building the LPM of the automobile, realizes to quickly evaluate and correct a primary design proposal, and enables the design period to be shortened.
Description
Technical field
The invention belongs to Automobile Body Design technical field, relate to a kind of automobile front structure head-on crash Conceptual Model Design method, specifically, relate to a kind of automobile front structure head-on crash Conceptual Model Design method based on lumped parameter model.
Background technology
Body structure design is divided into conceptual design and two stages of detailed design usually.The main task of frontal crash of vehicles conceptual phase determines arrangement form and the minibus Stiffness Distribution of vehicle body energy absorbing component.Body structure, as one of large assembly of automobile four, is the important component part in Automobile Design, is also the important carrier ensureing Crash Safety Design of Vehicles energy simultaneously.Structure minibus is as the important indicator evaluating vehicle safety performance, the difficulty of its design is large, the leeway of modifying at automobile detailed design phase is less, therefore at conceptual phase by the crashworthiness of automobile as design object, for raising complete automobile collision security performance, shorten product design cycle tool and be of great significance.
By retrieving pertinent literature, domestic and international each research institution all carries out large quantity research to the automobile concept design.It is the FOA system of operating platform that the people such as the Hidekazu Nishigaki of Toyota Company develop with EXCEL, with the car body frame structure rapid modeling of real concept design phase.The people such as the KarimHamza of technique center, Nissan North America, establishing the Auto-Body Conceptual comprising sliding pair and revolute pair designs a model, and has carried out simulation analysis.The designer of Ford Motor Company develops a kind of concept car body frame structure; The people such as the Nicklas Bylund of Volvo motor corporation develop DAMIDA program and ADRIAN program, be respectively used to set up beam element and connector unit, and apply these two kinds of programs and establish the Auto-Body Conceptual model PBM (Property-Based Model) comprising joint stiffness matrix and beam element cross section information, this model has been applied to the conceptual design exploitation of Volvo platform vehicle type.The Xu Tao professor team of Jilin University and designer's joint research of China No.1 Automobile Group Co technique center develop the dedicated analysis instrument being applicable to the Auto-Body Conceptual design phase, be integrated with rapid modeling, stiffness analysis, DOE and multiple optimized algorithm, achieve the rapid modeling of conceptual phase car body frame structure simplified model, analysis and optimization.
Find out that conceptual design model must meet following 3 requirements from above analysis: (1) model must be simple, do not having the conceptual phase of detailed vehicle body data can be easy to structure, thus express-analysis is realized to the rationality of body structure; (2) model will conveniently be revised, and by the rationality of simplified model analysis contrast design scheme, its final purpose is the optimization of body structure, if simplified model does not meet the requirement of Modify rapidly, then can not be applicable to conceptual phase; (3) model is also wanted to realize parametrization, parameterized modeling method can ensure to realize only needing the partial design parameter revising model just can adapt to the object of new model function, on the other hand, the simplified model set up by parametrization can the real concept design phase optimal design vehicle design the initial stage introduce optimize concept, ensure the rationality of Conceptual Design from the source of design, avoid the amendment repeatedly of detailed stages.
Lumped parameter model LPM (Lumped Parameter Model) is well positioned to meet above 3 requirements.In similar prior art, the spring unit of car load LPM all adopts resilient material, and this can cause mass generation resilience in collision process, occurs corresponding error.Further, in prior art, force-displacement relationship curve rigidity assignment is carried out to the spring unit of LPM and mostly define according to test figure or analog result, belong to reverse conceptual design, little to the directive significance of new model detailed design phase.The main advantage of LPM is, in the automobile concept design stage, according to general arrangement demand Modify rapidly LPM design parameter, thus can be distributed with a design quantized to part quality and vehicle body axial rigidity, the degree of freedom of design is large, realizes the conceptual design of forward.
Summary of the invention
In order to solve problems of the prior art, the invention provides a kind of automobile front structure head-on crash Conceptual Model Design method, be a kind of lumped parameter model LPM (Lumped ParameterModel) of simplification, be mainly used in the layout research of minibus analysis in the forward conceptual phase of new model and vehicle body front structure.By setting up the multiple degrees of freedom LPM of new model, carrying out express-analysis evaluation automobile and showing at the minibus of head-on crash process, and can instruct further and the vehicle structure optimal design of carrying out based on security.By by the piecewise linear force-displacement relationship curve assignment of parameterisable to the spring unit in LPM, realize the definition of LPM axial impact rigidity, by the non-linear Moment Rotation family curve assignment of parameterisable to torsionspring, the flexural deformation of simulation plastic hinge, thus reach automobile conceptual phase entry evaluation crashworthiness, control the design object of the distribution of vehicle body axial rigidity, car load flexural property.
Its technical scheme is:
A kind of automobile front structure head-on crash Conceptual Model Design method, comprises the following steps:
Step 1: designer carries out overall design to the automobile front structure of conceptual phase, determines major parameter and the layout of automobile;
Step 2: designer, according to the needs of frontal crash of vehicles security actual design problem, determines scale and the shape of LPM, i.e. number of degrees of freedom, the Space Layout Structure of model, namely the physical size, position etc. of automotive front endergonic structure subsystems;
Step 3: according to above information, carry out integrated to Full Vehicle System and simplify, by its abstract be lumped parameter model LPM, wherein, comprise the spring unit that the parts that energy-absorbing subsystem or parts are occurred in axial conquassation are reduced to elastic-plastic, being reduced to plastic hinge structure by there are the parts of plastic bending deformation, by large deformation not occurring in collision process or not bearing the large quality structure of energy-absorbing task, being reduced to the mass unit of rigidity;
Step 4: according to general arrangement situation and the design object of target vehicle, determine the practical significance of each unit representative in car load LPM, i.e. the design parameter of spring unit and mass, comprises its length, the mass length of side and mass quality;
Step 5: according to expecting the minibus target that will reach in Conceptual Design, each rigidity situation of axial conquassation spring, the flexural property of moulding flexural spring in design car load LPM, according to design experiences and designing requirement, design definition is carried out to the piecewise linear force-displacement relationship curve, the moment-rotation relation that represent each spring rate, then gives corresponding elastic-plastic spring material by family curve assignment;
Step 6: the design parameter in model, realize parametric modeling, finally realizes whole process robotization, and namely modeling is to the operating in a key solved;
Step 7: the car load LPM established is imported in general business software and carries out head-on crash simulation analysis, obtain the object information of car load LPM, comprise: impact force, energy and the speed curve in time domain, judge whether the collision response of car load LPM meets predefined Frontal Crash Safety of HF designing requirement accordingly, if do not met, design parameter then in design allowed band in application development platform amendment LPM, comprise its length, the rigidity of mass quality and spring, until meet design requirement, conceptual phase terminates since then, and the detailed design of vehicle structure can be carried out on this basis.
Preferably, major parameter described in step 1 and layout comprise length of wagon, width, height and complete vehicle quality etc.
Preferably, design parameter described in step 6 is the length, rigidity, space layout etc. of parts.
Compared with prior art, beneficial effect of the present invention is:
The present invention is by this automobile front structure head-on crash conceptual design method based on lumped parameter model, can according to overall layout requirements fast construction complete automobile collision conceptual analysis model, realize the rapid evaluation of crashworthiness, and then instruct follow-up structural modification and arrange adjustment, meet the structural design demand towards passive security performance.Designer adopts the present invention, can realize the rapid evaluation of car load crashworthiness in preliminary project and the Modify rapidly of design proposal.There is stronger practicality.
Accompanying drawing explanation
Fig. 1 is the process flow diagram that LPM of the present invention implements;
Fig. 2 is the position view of plastic hinge structure in LPM, and wherein, Fig. 2 a is LPM axonometric drawing of the present invention, and Fig. 2 b is LPM side view, illustrates the schematic diagram that Fig. 3 is plastic hinge structure in LPM of the present invention;
Fig. 4 is the preparation method of the force-displacement curve of non-linear rigidity, and wherein Fig. 4 a is force-time curve, and Fig. 4 b is displacement-time curve, and Fig. 4 c is the force-displacement curve of force-time curve and displacement-time curve matching;
Fig. 5 is Comparative result analysis, and it is the contrast of the LPM of certain true A type car and the collision response of its car load finite element detailed model, and wherein Fig. 5 a is the analysis contrast of Velocity-time, and Fig. 5 b is the analysis contrast of kinetic energy-time.
Embodiment
Below in conjunction with the drawings and specific embodiments, technical scheme of the present invention is described further.
Fig. 1 is the process flow diagram of the frontal crash of vehicles conceptual design method that the present invention is based on lumped parameter model, and it comprises following concrete steps:
Step 1: designer carries out overall design to the vehicle structure of conceptual phase, determines major parameter and the structure of automobile, as length of wagon, width, height and complete vehicle quality etc.
Step 2: designer, according to the needs of frontal crash of vehicles security actual design problem, determines scale and the shape of LPM, i.e. number of degrees of freedom, the Space Layout Structure of model, i.e. the physical size, position etc. of body forward structure endergonic structure subsystems; Demand due to true vehicle A conceptual phase only considers the axial rigidity definition of main energy absorbing component, the moulding flexural property of component home and the quality influence of large mass rigid structure; and do not plan to realize the simulation to passenger protection function at conceptual phase; therefore the number of degrees of freedom, of the car load LPM of vehicle A is designed to 8, sets up the double symmetrical LPM model of simplification with plastic hinge structure.
Step 3: according to above information, to Full Vehicle System carry out integrated and simplify, by its abstract be lumped parameter model LPM.Wherein, comprise main energy-absorbing subsystem or parts, as bumper and energy-absorption box assembly, front vertical straight beam, front vertical curved beam, beater or beat-up, upper straight beam etc., be reduced to the spring unit of elastic-plastic, the coupling part of plastic bending deformation will occur, the coupling part of front longitudinal will replace with plastic hinge model, will large deformation not occur in collision process or not bear the large quality structure of energy-absorbing task, as engine, wheel box, part crossstructure, be reduced to the mass unit of rigidity.
Fig. 2 illustrates the car load eight degrees of freedom LPM of true vehicle A, and wherein each mass reduction situation is expressed as follows: M1 is the quality of bumper and energy-absorption box; M2 is the quality of subframe, suspension system and wheel; M3 is the quality of upper straight beam beater or beat-up; M4 is the quality of engine and wheel box; M5 is body quality.For each mass, only consider this freedom of motion of vehicle body axial direction.Energy absorbing component in car load LPM representated by each spring unit or the situation of subsystem as follows: K1 is bumper and energy-absorption box assembly; K2 is front longitudinal first paragraph; K3 is front longitudinal second segment, and it is plastic hinge structure; K4 is upper straight beam; K5 is beater or beat-up; K6 is engine clearance.
In LPM model degree of freedom, according to the specific requirement of conceptual phase safety Design, can increase or reduce the degree of freedom of LPM.Such as, at conceptual phase as the response characteristic of occupant in collision process need be considered, then can set up the mass representing occupant and corresponding restricted spring in LPM.
Step 4: according to general arrangement situation and the design object of target vehicle, determine the design parameter of each spring unit and mass in car load LPM, comprise its length, the mass length of side and quality.
The final design parameter situation of the car load eight degrees of freedom LPM of vehicle A refers to table 1, table 2, and wherein in subordinate list 2, K3 is plastic hinge structure, and front vertical curved beam is divided into the length of three sections (L1, L2, L3) to be respectively 25mm, 335mm, 25mm.
Step 5: according to expecting the minibus target that will reach in Conceptual Design, the rigidity situation of each spring in design car load LPM: first according to design experiences and designing requirement, to the piecewise linear force-displacement relationship curve representing each spring rate carry out design definition, then by curve assignment to the spring material of elastic-plastic.
Each mass cell parameters in table 1 double LPM model
Each spring unit parameter in table 2 double LPM model
Fig. 3 illustrates plastic hinge structure, contains the identical node of two volume coordinates at the plastic hinge place of model, belongs to two adjacent beam elements respectively.Between the node that these two positions overlap, set up torsionspring unit, be used for simulating front longitudinal serpentine and bend, the moment of flexure obtained by theory deduction and angle relation family curve are assigned to this torsionspring.Use cylindricality hinge to ensure the conode at plastic hinge place simultaneously, plastic hinge place can only be relatively rotated, can not relative movement be produced, meet moulding bending deformation behaviour.
Step 6: the car load LPM established is imported in general business software and carries out head-on crash simulation analysis, obtain the object information of car load LPM, comprise: impact force, the curve in time domain such as energy and speed, judge whether the collision response of car load LPM meets predefined Frontal Crash Safety of HF designing requirement accordingly, if do not met, in design allowed band, then revise the design parameter in LPM, comprise its length, the rigidity of mass quality and spring, until meet design requirement, conceptual phase terminates since then, and the detailed design of vehicle structure can be carried out on this basis.
Fig. 4 illustrates the method obtaining nonlinear stiffness curve force-displacement curve: carry out by parameterized thin walled beam force-time curve that axial conquassation l-G simulation test obtains, displacement-time curve matching obtains.
Above step is all by parametric modeling mode realization flow automated analysis.
Fig. 5 a, Fig. 5 b respectively illustrate the LPM collision response that is applied to certain true vehicle A conceptual phase exploitation and based on this LPM model, carry out the comparative analysis result between car load finite element detailed model that body structure detailed design finally obtains.Wherein solid line is the response that detailed model obtains, and dotted line is the response that LPM model obtains.Although as can be seen from the figure LPM collision response numerically exists certain deviation with detailed model result, overall variation rule is comparatively close.Therefore, the LPM of conceptual phase has guiding value to frontal crash of vehicles performance design.
The above; be only the present invention's preferably embodiment; protection scope of the present invention is not limited thereto; anyly be familiar with those skilled in the art; in the technical scope that the present invention discloses, the simple transformation of the technical scheme that can obtain apparently or equivalence are replaced and are all fallen within the scope of protection of the present invention.
Claims (3)
1. an automobile front structure head-on crash Conceptual Model Design method, is characterized in that, comprise the following steps:
Step 1: designer carries out overall design to the automobile front structure of conceptual phase, determines major parameter and the layout of automobile;
Step 2: designer, according to the needs of frontal crash of vehicles security actual design problem, determines scale and the shape of LPM, i.e. number of degrees of freedom, the Space Layout Structure of model, the namely physical size of automotive front endergonic structure subsystems, position;
Step 3: according to above information, carry out integrated to Full Vehicle System and simplify, by its abstract be lumped parameter model LPM, wherein, comprise the spring unit that the parts that energy-absorbing subsystem or parts are occurred in axial conquassation are reduced to elastic-plastic, being reduced to plastic hinge structure by there are the parts of plastic bending deformation, by large deformation not occurring in collision process or not bearing the large quality structure of energy-absorbing task, being reduced to the mass unit of rigidity;
Step 4: according to general arrangement situation and the design object of target vehicle, determine the practical significance of each unit representative in car load LPM, i.e. the design parameter of spring unit and mass, comprises its length, the mass length of side and mass quality;
Step 5: according to expecting the minibus target that will reach in Conceptual Design, each rigidity situation of axial conquassation spring, the flexural property of moulding flexural spring in design car load LPM, according to design experiences and designing requirement, design definition is carried out to the piecewise linear force-displacement relationship curve, the moment-rotation relation that represent each spring rate, then gives corresponding elastic-plastic spring material by family curve assignment;
Step 6: the design parameter in model, realize parametric modeling, finally realizes whole process robotization, and namely modeling is to the operating in a key solved;
Step 7: the car load LPM established is imported in general business software and carries out head-on crash simulation analysis, obtain the object information of car load LPM, comprise: impact force, energy and the speed curve in time domain, judge whether the collision response of car load LPM meets predefined Frontal Crash Safety of HF designing requirement accordingly, if do not met, design parameter then in design allowed band in application development platform amendment LPM, comprise its length, the rigidity of mass quality and spring, until meet design requirement, conceptual phase terminates since then, and carry out the detailed design of vehicle structure on this basis.
2. vehicle structure head-on crash Conceptual Model Design method according to claim 1, it is characterized in that, major parameter described in step 1 and layout comprise length of wagon, width, height and complete vehicle quality.
3. vehicle structure head-on crash Conceptual Model Design method according to claim 1, is characterized in that, design parameter described in step 6 is the length of parts, rigidity, space layout.
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| CN107256289A (en) * | 2017-05-18 | 2017-10-17 | 吉林大学 | The method for building up of car crass reduced parameter FEM model |
| CN108829976A (en) * | 2018-06-20 | 2018-11-16 | 吉林大学 | A kind of car steering stability region of many-degrees of freedom system determines method |
| CN109002642A (en) * | 2018-08-08 | 2018-12-14 | 中车长春轨道客车股份有限公司 | The quick design optimization method of vehicle body of railway vehicle chassis front end endergonic structure |
| CN109800494A (en) * | 2019-01-14 | 2019-05-24 | 湖南大学 | Vehicle body forward direction conceptual design method based on thin wall section attribute |
| CN113704865A (en) * | 2021-07-15 | 2021-11-26 | 江铃汽车股份有限公司 | Crash-proof analysis method for main transmission path bearing component of composite material reinforced whole vehicle |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN113704865A (en) * | 2021-07-15 | 2021-11-26 | 江铃汽车股份有限公司 | Crash-proof analysis method for main transmission path bearing component of composite material reinforced whole vehicle |
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Application publication date: 20150429 |