注塑机的动态模拟毕业课程设计外文文献翻译

1、附录adynamic simulation of an injection moldingauthorl, author2, author3.applied thermal engineering, 2016, 8(6):556-568.abstract: an integrated design method is discussed which thoroughly considers related parameters of the various subsystems in order to optimize the overall system that mainly consis

2、ts of opto-mechanical structure cad, cae and the integrated information platform pdm. based on the parameter drive of the virtual main model, the method focuses on the model tra nsformatio n and data share among d if fere nt design and analysis steps, and so the concurrent simulation and design opti

3、mization are carried out. as an example of application, the integrated design for a large-scale opto-mechanical structure is introduced, including optical design, structure design and analysis, which further validates the advantages of the method. due to comprehensive consideration of the design and

4、 analysis process by cad and cae based on pdm, the integrated design well attains the structure optimization with high efficiency.keywords: integrated design; cad/cae; large-scale structure; optical instrument.1. introductionthe an alysis of products in tegrati ng d iff ere nt tech no logies, e.g. m

5、echanical, hydraulic and controls systems, becomes more and more feasible with the constant development of simulation software and more performing computer hardware. the combination of specialized software packages is possible and allows the simulation of so-called mechatronic systems. if in the pas

6、t such tools were mainly used in the aeronautic and automobile industries, they now find their way into more common engineering applications. in this case,the dynamic characteristics of the clamp unit of an injection molding machine from husky is investigated. for this purpose, the finite-element (f

7、e) program ansys, the multi-body simulation (mbs) software adams, the fluid power simulation software dshplus and the controls design tool matlab/simulink are used. combining these different simulation tools and applying them to the damp unit, we can analyze and un d erst a nd the dyn amic behavior

8、of the machine and the interaction between the different sub-systems. this is necessary to improve the performsnces, like reducing wear, cycle time or noise, or avoiding premature failure of parts.the damp unit is the mechanism that doses and opens the mold and keeps it effectively closed during the

9、 injection and the holding-pressure stages. the husky ouadloc' damp is a two-platen hydraulic damping system. the main components are the moving platen, the clamp base and the stationary platen with the four tie bars. the platen locking and the damping force are realized with the damp pistons, w

10、hich are integrated in the moving platen. the damp pistons can be rotated by 45' to engage the tie bar teeth in order to lock the moving platen in its position. the main functions of the damp unit are actuated hydraulically;hydraulic pressure is applied to the damp pistons to generate the necess

11、ary damping force and two hydraulic cylinders are used for the displacement of the moving platenfigurel: husky quadloc clamp unitthe analysis focuses on two aspects: first, the quantification of the forces acting on the pads between the damp base and the foundation in order to foresee and prevent an

12、y creep of the machine during operation, and seconct the optimization of the stroke comma nd signal in order to reduce the overall cycle time. therefore the simulation model is limited to the moving platen stroke.2. simulation modelsthe mechanical, hydraulic and controls systems are modeled in adams

13、, dshplus and matlab/simulink, respectively. adams gives the possibility to include norvstandard phenomena by linking user-written fortran or c subroutines in the model. dshplus uses this feature to make a co-simulation between both programs possible. besides, adams disposes of a plug-ln that allows

14、 the user to conned the mbs model with simulink. thus it is possible to link the three simulation tools and simulate the complete machine. there are two possibilities for the computation: first, each program integrates its own set of differential equations and exchanges the necessary parameters with

15、 the other ones, second, the three models are completely integrated and only the slmulink solver integrates the differential equations set.simulink|adams|dshplusposition of moving platenforce of cylindersposition of cylinders velocity of cylinders command signalcommand signal!lfigure2:co-simulation

16、of moving platen strokeadditi onally, the flexibility of mecha nical parts can be in eluded in adams. we use ansys to gen erate the n ecessary fe models and to reduce these large models to a few degrees of freedom before being integrated into adams. the reduction method is based on the component mod

17、e synthesis technique introduced by craig and bampton.mechanical modelthe rgid-body model of the damp unit is very simple and con si sts only of two parts: the moving platen and the stati on ary plate n with damp base and tie bars (refer to figure 4). the damp base is fixed with linear spring-damper

18、 elements to the ground and the sliding of the moving platen is modeled with contact statements. basically, the con tact stateme nt is a nonlin ear spri ng-damper elernie nt where the force is proportional to the penetration depth x and the penetration velocity it:xk and d are the con tact stiff nes

19、s and dampi ng coefficie nts, respectively and a is an exp orient that for nu merical reas ons should be chose n greater the n 1. if there is no penetration, then no force is applied, otherwise the location of contact, the normals at the points of contact and the force acting between both parts are

20、computed. the statement also includes a coulomb friction model. the transition from the static to the dynamic friction coefficient is based on the relative velocity of the two collidi ng geometries. finally, the two stroke cylinder forces and a con tact stateme nt are defi ned betwee n both plate ns

21、. in order to have a more accurate mechanical model, also in view of a more realistic distribution of the forces on the damp-base pads, the different parts are in eluded as flexible bodies. these flexible bodies are derived from fe models that are reduced before being imported. the reduction method

22、implemented in adams is based on the component mode synthesis (cms) technique, i.e. the deformati on is written as a lin ear combi nation of mode shapes. in adams, constraint modes and fixedboundary normal modes are used to gen erate the comp onen t-made matrix 0. this approach is know n as the crai

23、g-bampton method. in the following, the basic principles and steps of integrating flexible bodies in adams are shown; a more detailed theoretical presentation can be found infirst of all, a fe model is created that is detailed eno ugh to comedy represe nt the mode shapes of interest. the user has th

24、en to choose the nodes that serve as interface to the mbs model. the kinematic constraints or forces are applied to these boundary no des; the remai ning no des are referred to as in terior no des by fixing the degrees of freedom (dof) u, of the boundary nodes and solving an elgenproblem, we get the

25、 fixed-bounder, normal modes d>r. this normal mode set is usually truncated the constraint modes de are defined as the static deformation of the structure when a unit displacement is applied to one dof of a boundary node while the remai ning dof of the boun dary no des are restrai ned (guya n red

26、ucti on). finally the comp orient mode reduction matrix m is defi ned by the no rmal modes set c|)and the constraint modes set d>r.the relati on ship betwee n the physical displacement coordi nates u and the component generalized coordinates q is°t么with equati on (2) the gen erally large nu

27、mber of physical dof u is drastically reduced to few mixed physical and modal dof q.however, the craig-bampton modal basis q has certain disadvantages that make it sometimes difficult to directly use it in a multi-body simulation. the set of constraint modes contains the 6 rigid-body dof that must b

28、e replaced by the large displaceme nt dof of the local body ref ere nee frame in adams they have to be removed and therefore the component-mode matrix is transformed by solving the eige nproblemkq - amqwhere k and m are the reduced stiffness and mass matrix, respectively. the manipulation results in

29、 a modal basis where q n4; n containing the elgenvectors from equation (3).a人人u =啊=(pn q = © qthe last step is a purely mathematical approach and does not further reduce the number of dof. the new modal basis q has no direct physical meaning anymore but addresses the problems mentioned abovetab

30、le 1: first 13 eigenfequencies of the moving platen/t、ta 1= x y z iff & 丿the motion of a flexible body is derived from the same equation as for a rigid-body, l.e. lagrange's equations. in order to calculate the kinetic and potential energy, the position and velocity of an arbitrary point on

31、the flexible body is expressed with the generalized coordinates.<s 3 k： +d：+呎几=qmthe generalized mass matrix depending on,k the generalized stiffness matrix only depending on qv the gravitational energy,d the damping matrix defined using modal damping ratios isq the kinematic constraint equations

32、 applied to the flexible bodyadding flexible bodies to an adams model is quite straightforward. nevertheless, there are some limitations regarding forces and joints that can be defined to them. especially the problem of a moving force on a flexible body.i.e. moving platen sliding on clamp base, is a

33、n open issue in multi-body dynamics. however, there are "standarct workarounds which work well and which have proven their usefulness.the tech nique impleme nted in our flexible-body model is based on the con tact statement mentioned above. basically it works as follows: for each of the selecte

34、d no des along the slidi ng path, a force is computed according to equati onthat depends on the relative vertical position y and velocity y of the node to the moving platen.however, the force is only activated when the node and the moving platen effectively overlap. in fad, it is weighted by a funct

35、ion that depends on the horizontal distanee x between the node and the moving platen.the force is ramped up from zero or ramped down to zero in order to guarantee a smooth application and to minimize any discontinuities.no con tact points and con tact normals are computed. the distance and velocity

36、of a node relative to the moving platen are taken in the global coordinate system and the contact and frictio n forces are always colli near with the coordi nate system unit vectors.nevertheless, this approach gives acceptable results, as the deformation of the damp base is very small. a coulomb fri

37、ction force is applied in the same way.weighting function for a nodefigure 3: moving platen sliding modelthe main disadvantage is that a huge nu mber of in terface nodes are n eeded to have any sound represe ntati on of the moving con tact forces. unfortun ately, this gives a huge number of flexible

38、-body dof and therefore unacceptable computation times. now, instead of defini ng these no des as interface nodes, they remai n in terior no des. from a purely theoretical point of view, the accuracy of the results is not guaranteed any more whe n using in terior no des as interface nodes. however,

39、choosing more normal modes can reduce the error. the comparison of a model using in terior no des for the movi ng plate n slidi ng with one using in terface nodes shows avery 9000 compliance of the results while having a much taster computation time. therefore we used this model for the following si

40、mulations. other methods were not tested but some of them are presented in (3) and (4).the flexible bodies are created in ansys simplified cad geometries of both platens were imported in the fe program and meshed automatically with tetrahedral solid187 eleme nts. the damp base was gen eratednually”

41、with shell63elements and the tie bars are modeled with beam4 elements. stationary platen, clamp base and tie bars were put together b one assembly and the different components connected via spring-damper elements (combin14). a macro for the computation of the modified craig-brampton basis is availab

42、le in ansys. it allows the user to specify the in terface nodes and the nu mber of normal modes. the resulting modal basis is written to a file that has to be imported into adams.the ansys macro automatically selects the six dof of each interface node as u. however, it is not imperative to select al

43、l the six dof. this allows us to furthermore reduce the number of static modes and thus the number of flexible-body dof. the macro has been changed accordingly to select only the effectively required dof ua finally, the movi ng platen has 29 flexible-body dof and the stati on ary platen, clamp base

44、and tie bars assembly has 95 flexible-body dof.cxxitact element tie bar - moving platentie barstationary platencnntact element between platens-sliding- contact elementmoving platenspring<jamper elementdamp basehydraulic forcefigure4:adams flexible-body model附录b注塑机的动态模拟authorl, author2, author3.ap

45、plied thermal engineering, 2016, 8(6):556-568摘要：讨论了充分考虑相关的参数是一个集成的设计方法为各子系统优化的整体 系统，主要由光电一机械结构cad, cae与pdm集成信息平台。基于的虚拟模 型的参数驱动的方法，侧重于模式的转型的设计和分析的步骤z间的数据共享, 所以并行仿的设计进行优化。作为应用实例，综合设计介绍了一种大型光学机械 结构，包括光学设计，结构设计与分析，进一步验证了该方法的优点。由于分析 了基于pdm和cad和cae过程的设计，集成设计达到结构优化效率高。关键词：集成设计：cad/cae：大规模的结构：光学仪器1. 介绍产品整体不

46、同技术的分析，例如，机械、液压、控制系统，模拟软件可持续 发展和更多计算机硕件操作变得越来越可行。结合特殊的软件程序包是可以和允 许对所谓的机电一体化系统模拟的。如果在过去这些工具被应用与航空和汽车工 业中，那么他们现在会找到更多应用工程技术的相同点。因此，被研究的是husky 注塑机夹紧装置的动态特性。ansys有限元(fe)程序，adams多维模拟软件， dshplus流体动力模拟软件和matlab仿真设计控制工具都被用于这个fl。结合 这些不同的模拟工具并应用它们于合模机构，我们就能分析和理解机器的动态行 为和不同子系统之间的联系。这就需要去提高性能，像减少磨损、循环时间或噪 音，或者避

47、免部件早期的错误。合模机构是一个开启与合上模具并能够在注塑和保压阶段有效的紧闭的机 构。husky quadloctm合模机构是一个二板式液压合模系统。主要由动模板, 合模工作台，定模板和四个拉杆构成。模板锁定和合模压力是通过动模板整合的 合模栓塞实现的。合模栓塞可以旋转45度去啮合拉杆螺纹为了保证动模板在注 塑位置上。合模机构的主要功能是驱动液压油：液体压力被施加在合模栓塞上去 产生需要的合模压力并口两个油缸被用于动模板的移动。分析的焦点集屮在两个方面：第一，压力作用在工作台z间的衬垫上和为了 预见的基础并阻止机器在运转中爬行。第二，为了减少总体循环时间的最优化的 喷射控制信号。因此，模拟模

48、型被限制移动模版的注射。2. 模拟模型机械，液压，控制系统被分别的在adams, dshplus和matlab仿真屮模拟。 adams可能包括由链接fortran书面使用和c程序在模型中引起的不标准的现 象odshplus利用这个特点在两个可能的程序上建立了一个co模拟。另外,adams 处理插件允许使用者用模拟链接mbs模型。因此，链接三个模拟工具和模拟整 个机器是可能的。这里有两个可能估计：第一。各个整合它自己不平衡的部分并和其他的部分交换参数。第二，三个模型被完全的整合并只有模拟求解整合不同 的因素部分。mb融合模琲台负模航动朋图1 husky quadloctm合模机构此外，柔性的机械

49、部件可以包括在adams中。我们用ansys产生必耍的fe 模式，并在被纳入adams之前降低这些大型模型自由度。减少自由度方法是基于引用craig和bampton的组件式合成技术这是必要的。动模板的位置油缸压力 控制信号 油缸位置 油缸速度 控制信号图2模型的联合仿真2 力学模型ui合模机构的刚性模型很简单，只分为两个部分：移动模板和固定模板和合模 工作台还有拉杆（参见图4）。合模工作台是同定在地面上装有线性弹簧阻尼单 元和滑动的动模板构成报表式的模型。基木上，报表式是一个穿透深度x和渗透 速率x与压力成正比的非线性弹簧阻尼单元k和d分别的是接触刚度和阻尼系 数，e是一个指数，由于数值原因应选择大于1。如果没有渗透，那么就没有压 力作用，否则就会有接触，正常应在接触点和作用力两部分之间计算。该报表还 包括了一个库仑摩擦模型。从静态到动态的摩擦系数的变化，是基于相对速度的 两个几何碰撞。最终，在两个模板之间定义了两个液压缸的压力和接触报表。为 了有一个更准确的力学模型，同时，鉴于更为实际的分配作用在合模工作台