機(jī)械畢業(yè)設(shè)計(jì)-400方車(chē)銑轉(zhuǎn)復(fù)合滑枕設(shè)計(jì)（全套含CAD圖紙）,機(jī)械,畢業(yè)設(shè)計(jì),方車(chē)銑轉(zhuǎn),復(fù)合,設(shè)計(jì),全套,cad,圖紙 Optimal Design of Compliant Trailing Edge for Shape Changing Abstract: Adaptive wings have long used smooth morphing technique of compliant leading an d trailing edge to improve their aerodynamic characteristics．This paper introduces a systematic approach to design compliant structures to carry out required shape changes under distributed pressure loads．In order to minimize the deviation of the deformed shape from the target shape，this method uses M ATLAB and ANSYS to optimize the distributed compliant mechanisms by way of the ground approach and genetic algorithm (GA)to remove the elements possessive of very low stresses．In the optimization process，man y factors should be considered such as air loads，input displacements，and geometric nonlinearities。Direct search method is used to locally optimize the dimension an d input displacement after the GA optimization。The resultant structure could make its shape change from 0 to 9．3degreesTheexperimental data of the model confirm s the feasibility of this approach． Keywords： adaptive wing；compliant mechanism；genetic algorithm ；topology optimization；distributed pressure load；geometric nonlinearity 1 Introduction： As conventional airfoil contours are usually designed with specific lift coefficients and M ach numbers，they could not change in accordance with the environment changing．Siclari and Austin indicated that the variable camber trailing edge would produce the drag about sixty percent less than the conventional fixed camber airfoil There are three methods used to design able camber wings．Of them．one is conventional hinged mechanism，which，however, will create discontinuities over the wings surface leading to earlier airflow separation an d drag increase． The others are smart material and the compliant mechanism，of which both could realize smooth shape changing．Nevertheless，compared to the compliant mechanism，the smart—material—made actuators have many disadvantages，such as deficient in energy ,slow in response，strong in hysteresis，limited by temperature，and difficult to control too many actuators．Musolff from Industry University of Berlin used Ni—Ti shape—memory—alloy wire to make an adaptive variable camber wing，which could quickly change its shape，but could not perform highly frequent alteration because of its resilience depend en ton the heat exchange with the outside environment。 Compliant mechanism is a kind of one-piece flexible structure，which can transfer motion and power through its own elastic deformation．It is not only flexible enough to deform，but also has enough stiffness to withstand external loads．Thanks to its joint—free nature，it does not have the trouble some problems confronted by conventional mechanism such as friction，lubrication，noise and recoiling，thereby achieving smooth shape changing. In 1 994，Kota，a professor from University of Michigan，firstly pointed out that compliant mechanism could be used to control static shape changing under the sponsorship of the Air Force Of ice of Scientific Research in USA．Saggere and Kota suggested a new method to design compliant adaptive structures，which made the least square errors between the shape—changed curve and the target curve as the objective function for optimization．Based on their work，Lu put forward a load path representation method．However, her work was limited to only linear analysis under consideration of nodal loads．Good[ from Virginia Polytechnic Institute of State University used the compliant mechanism and the Moving Asymptotes method to design the fuselage tail within the allowable range of its tip maximal deflection．Kota and He trick in2004 designed a compliant trailing edge on the base of the F16s data，which can change from 0。to 15。and obtained a patent．Campanile from German Aerospace Center presented a modal procedure to design synthetic flexible mechanisms for airfoil shape control，and pointed out that the future re—search should take into account the air load and the geometric nonlinearity．Buhl from Riso National Laboratory of the Wind Energy Department in Denmark used the SIM P method and geometrically nonlinear finite element method to design compliant trailing edge flaps．FlxSys Inc in 2006 produced an adaptive compliant wing，which stood the test on the White Knight airplane．The results indicated that the compliant trailing edge could change+10 ．In China，the research of adaptive wing has been concentrated on smart material and conventional mechanism．Few people，it seems，have worked on designing adaptive wings with the compliant mechanism．Yang is an exception．He analyzed the active aero—elastic wings based on the aero—servo— elasticity technology．Chen and Huang separately investigated the morphing of the compliant leading edge from the viewpoints of discreteness and continuity. This paper presents a method to design the shape changeable structure by MATLAB and AN—SYS associated with distributed compliant mechanism on the base of the ground structure approach and genetic algorithm (GA)taking into account the external distributed loads and geometric nonlinearity. 2 Optimization Process: 2．1 Defining the trailing edge model and objective function As shown in Fig．1，both curves represent two ideal shapes of the trailing edge in the different flying states．One side point)of the structure is supposed to be fixed，and the other side point) to be sliding horizontally. Firstly, the design domain should be defined by the initial curve shape．the input location and the boundary conditions．Then．it is divided with abeam element network simulating the bird’s feather as shown in Fig．2．This is termed the partial ground structure method. Fig．1 Initial shape and target shape Fig．2 Discretization of the design domain The simplest and most effective way to manufacture the planar compliant mechanism is to use wire—cutting technology．In the optimization pro—gram，all the elements are of rectangular beams with the same width equal to the thickness of the material，every beams height being a design variable． In order to make the structure’s deformation come close to the target shape curve，the least square error(LSE)between the deformed curve and the target curve is defined as the objective function．LSE is the sum of squares of position differences of various points along the curves Its expression is where I (=1，2，?，P)is the number of the points along the curves，P is the total number of points．a(chǎn)ndare the coordinates of it h node on the target and deformed boundary curve respectively． The constraints are Where J (=1，2，?， )is the number of elements，miss the tota1 number of elements，，hi the dimension variable，hmin and hmax are the lower and upper bounds of the element beam height for all elements with the value dependent on manufacturing，hb the height of the boundary elements， the maximumnoda1 deformation of the nodes on the curve boundary when the input point is inactive，and should be smaller than[d]to ensure structure stiffness，[d] the allowable maximum displacement when the input point is inactive，O'max the maximum stress of al1 the elements which must be smaller than Tj to prevent yielding，Tj the topology variable equal to 1，or else0 when the element is eliminated． 2．2 GA optimization GA is an optimization method which simulates the heuristic selection rule in nature，where the fit．test living things have the most chance to survive，but the inferior ones also have the opportunity to exist． Different from the continuous optimization method，it does not require the gradient-based in—formation of the objective function. Every element could be expressed as a topology variable and a dimension variable． There—fore，each individua1 could be coded as follows where ，2 is the number of elements except the boundary ones．With the same heights，the boundary elements throughout the optimizing process are represented by only one variable，hb. The fitness is the criterion of the GA optimization．It could be transformed from the objective function into where βis a coefficient deciding the compulsive selection of the betterindividua1．The smaller the value，the more different would be between the two individuals’fitness thus increasing the compulsiveness of choosing the individual of higher fitness． The selection of control parameters plays an important role in the convergence of the GA．Generally speaking．the cross probability ranges 0．40—0．99；the mutation probability is 0．000 01-0．01．a(chǎn)nd the number of individuals 1 0．200． The variable would be updated through the crossover and mutation，so the possible design could generate in the GA process． 2．3 Finite element analysis(FEA) Because of the limited design variables and the target function，the optimization module of FEA software could not be used to design the compliant morphing mechanism．Therefore，this paper programmed the GA in MATLAB and the FEA in ANSYS．In the FEA，taking only account of geo—metric nonlinearities and the material being of linear elasticity, ANSYS could solve the node displacements and the element stresses．Then by deleting the elements with low stress，the fitness could be calculated．Fig．3 shows the detailed process． Fig．3 Flowchart of the structural optimization program． 2．4 Second optimization Although the GA could optimize the topology and dimension simultaneously in a large solution space，the dimension usually could not directly converge to the optimization．In order to solve this problem，after the GA，the Direct Search method should be used to find the best values of the input displacement and the dimensions of the elements which remain in the results after the GA． For morphing of compliant mechanism，F(xiàn)ig．3describes the whole optimization process．It mainly contains initialization of the design domain，F(xiàn)EA，GA optimization and second optimization. 3 Presentation of Results: Adopted from Ref，the sizes of the initial and the target trailing edge are reduced by sixty percent．，I1ab1e 1 lists the design parameters. Because the displacement is used as the input，the nonlinear analysis could hardly converge and the stress of the initia1 solutions is very large．Which should be considered after thirtieth generation. Table 1 Design parameters Fig．4 and Fig．5 illustrate the results from the GA optimization and the second optimization respectively． Fig．4 Results after the GA optimization Fig．5 Results after the second optimization． Form Table 2，it could be found that through the second optimization of the input displacement and the dimension，the LSE is reduced by 1．352 8mmand improved by 3．13％ ．The altered angle is increased by 1．049 3 Table 2 Results after the two optimization Fig．6 Stability of final optimal structure Fig．6 shows the influences of the parameters when the outside distributed pressure load changes from 0 to 1 0 N／mm and the input displacement re—mains 1 1．389 7 mm on the optimal structure．It could be seen that the optimal structure has a good stability if the load is kept in the range Of 0—5 N／mm．As the external load exceeds 5 N／mm，the max stress is likely to exceed the yield stress． Because this optimization program is based on the M ATLAB and ANSYS．in order to verify the results．a(chǎn)n attempt is made to introduce the analytical results of the optimized structure into ANSYS and PATRAN respectively, and then a comparison is made between them．As shown in Fig．7 and Fig．8，the two altered shapes are in good agreement：for in ANSYS the tip displacement is 54．97mm and in PATRRAN 54．50mm．The minor difference between them is from the software． Fig．7 Results of FEA in ANSYS Fig．8 Results of FEA in PATRAN On the other hand，a model is made by wire—cutting technology to verify the analytical results．The material of the mode1．identical with that of the design，is 5 mm thick．In the experiment，the distributed pressure load is assumed to be zero．The input displacement 11．389 7mm with the required input load 146 N．Fig．9 shows the model and the experimental result．The altered angle is measured9．3。．a(chǎn)nd the tip displacement 53mm．The altered shape well accords to the optimized result．If a displacement of 11．3897mm is imposed on the model，the theoretical tip displacement is 54．796 mm． Be．cause of the friction there is between the model and the experiment table a tiny difference will take place between the measured data and the calculated results． Fig．9 The model and experimental result 4 Conclusions： Proved by the simulation and experiments，the proposed method to design morphing compliant mechanism is effectual in turning out a trailing edge with required morphing effects and ability of with—standing external loads．The combination of MAT—LAB and ANSYS in the optimization renders the program simple and universa1．There is no need for frequent changes of the rigid matrix．It also avoids the complexity of programming the nonlinear FEA and the transforming distributed loads into nodal loads．Using the mixed code，the topology and the dimension could simultaneously be optimized by the GA．Removing the free elements after the FEA could speed up the optimization．The second optimization could improve the GA results． 20 哈爾濱理工大學(xué)學(xué)士學(xué)位論文 400方車(chē)銑轉(zhuǎn)復(fù)合滑枕設(shè)計(jì) 摘 要 隨著經(jīng)濟(jì)建設(shè)的飛速發(fā)展，我國(guó)的工業(yè)需求正逐漸加大，世界上越來(lái)越多的復(fù)雜零件需要采用復(fù)合加工技術(shù)進(jìn)行綜合加工,滑枕是車(chē)銑轉(zhuǎn)復(fù)合機(jī)床中非常關(guān)鍵的部件，它帶動(dòng)刀具移動(dòng)，并給鏜、鉆、銑功能提供作業(yè)動(dòng)力?；淼慕Y(jié)構(gòu)和使用性能關(guān)系到機(jī)床的使用性能。此次設(shè)計(jì)對(duì)400方車(chē)銑轉(zhuǎn)復(fù)合滑枕進(jìn)行了詳細(xì)說(shuō)明和計(jì)算。設(shè)計(jì)的滑枕能夠滿(mǎn)足使用功能的要求，又解決了在起動(dòng)及制動(dòng)時(shí)的平穩(wěn)性問(wèn)題，能夠適用于許多工程建設(shè)，具有很強(qiáng)的現(xiàn)實(shí)意義。 本設(shè)計(jì)首先將要介紹車(chē)銑轉(zhuǎn)復(fù)合加工機(jī)床國(guó)內(nèi)外研究現(xiàn)狀、發(fā)展趨勢(shì)及研制中的關(guān)鍵技術(shù)，以及對(duì)復(fù)合滑枕進(jìn)行原理設(shè)計(jì)及結(jié)構(gòu)設(shè)計(jì)；確定主要結(jié)構(gòu)的技術(shù)參數(shù)，對(duì)結(jié)構(gòu)中的關(guān)鍵部分---絲杠進(jìn)行設(shè)計(jì)計(jì)算，并進(jìn)行驗(yàn)算校核，以保證其工作可靠性。 關(guān)鍵詞 ：復(fù)合加工技術(shù)；滑枕；液壓控制系統(tǒng)；結(jié)構(gòu) The Design Of 400 milling composite ram Abstract As the increasing development of the economic construction, our countries’ industrial demand is rising. Complex parts industry needs more and more of the world’s need for comprehensive. Ram is part composite machine tool is the key,it drives the cutter to move, and boring, drilling,milling function provides the power.The structure of ram and the use of performance relate to the use of machine performance.The design of the 400 milling composite ram in detail and calculation.The slippery pillow design to meet the functional requirements,but also solve the stability problem in starting and braking,can use many engineering construction,has the very strong practical significance. The first design will be the introduction of key technology research status,turn milling compound machine tool development trend at home and abroad and development, as well as the principle of design;determined the technical parameters main structure,the structure of the key part and the lead screw carries on the design and checking calculation,in order to ensure the reliability. Key words：Composite processing technology; Ram; Hydraulic control system; structure 目錄 摘 要 I Abstract II 第１章 緒論 1 1.1車(chē)銑轉(zhuǎn)復(fù)合加工機(jī)床 1 1.2車(chē)銑轉(zhuǎn)復(fù)合加工機(jī)床的優(yōu)點(diǎn) 1 1. 3國(guó)內(nèi)外現(xiàn)狀 2 1.4本課題主要研究?jī)?nèi)容 3 第2章 400方車(chē)銑轉(zhuǎn)復(fù)合滑枕總體設(shè)計(jì) 4 2.1 設(shè)計(jì)參數(shù) 4 2.2 電機(jī)的選擇 4 第3章 400方車(chē)銑轉(zhuǎn)復(fù)合滑枕機(jī)械結(jié)構(gòu)設(shè)計(jì) 6 3.1選擇齒輪材料及精度等級(jí) 6 3.2按齒面接觸疲勞強(qiáng)度設(shè)計(jì) 6 3.3軸類(lèi)零件的設(shè)計(jì) 10 3.3.1選擇軸的材料 10 3.3.2初算軸徑 10 3.4校核軸和軸承 10 3.5軸承壽命校核 13 3.6鍵的設(shè)計(jì)與校核 13 3.7 主軸組件要求與設(shè)計(jì)計(jì)算 14 3.7.1主軸的基本要求 14 3.7.2 主軸組件的布局 16 3.7.3主軸結(jié)構(gòu)的初步擬定 18 3.7.4主軸的材料與熱處理 19 3.7.5主軸的技術(shù)要求 20 3.7.6主軸直徑的選擇 20 3.7.7主軸前后軸承的選擇 21 3.7.8軸承的選型及校核 22 3.7.9主軸前端懸伸量 24 3.7.10主軸支承跨距 25 3.7.11主軸組件的驗(yàn)算 25 3.7.12主軸軸承的潤(rùn)滑 27 3.7.13主軸組件的密封 28 3.7.14軸肩擋圈 28 3.7.15撓度、轉(zhuǎn)角、鎖緊力的計(jì)算及校核 29 3.8 碟形彈簧的設(shè)計(jì) 30 3.8.1碟形彈簧的結(jié)構(gòu)尺寸 30 3.8.2彈簧的許用應(yīng)力和疲勞極限 31 3.8.3碟形彈簧的設(shè)計(jì)與計(jì)算 32 3.8.4碟形彈簧的校核 33 第4章 液壓原理圖和主體部分的計(jì)算 36 4.1 液壓原理 36 4.2 銑頭錐柄卡緊放松油缸的主要參數(shù) 37 4.3 銑頭拉釘卡緊放松油缸的主要結(jié)參數(shù) 37 4.4活塞桿強(qiáng)度計(jì)算 38 4.5 液壓缸活塞的推力及拉力計(jì)算 39 4.5.1銑頭錐柄卡緊放松油缸 39 4.5.2 銑頭拉釘卡緊放松油缸 40 4.6 活塞桿最大容許行程 41 4.7 液壓缸內(nèi)徑及壁厚的確定 41 4.8 液壓缸筒與缸底的連接計(jì)算 43 4.9 缸體結(jié)構(gòu)材料設(shè)計(jì) 43 4.10 活塞結(jié)構(gòu)材料設(shè)計(jì) 44 4.11 活塞桿結(jié)構(gòu)材料設(shè)計(jì) 45 4.12 活塞桿的導(dǎo)向、密封和防塵 46 4.13 缸蓋的材料 47 第5章 液壓系統(tǒng)設(shè)計(jì) 48 5.1系統(tǒng)液壓可以完成的工作循環(huán) 48 5.2 液壓執(zhí)行元件的配置 48 5.3 負(fù)載分析計(jì)算 48 5.4 液壓泵及其驅(qū)動(dòng)電動(dòng)機(jī)的選擇 49 5.5其他液壓元件的選擇 52 5.6 液壓系統(tǒng)壓力損失驗(yàn)算 55 結(jié)論 57 致 謝 58 參考文獻(xiàn) 59 - 4 -