ncode疲勞耐久性工程高級(jí)培訓(xùn)班課程基于有限元的虛擬壽命預(yù)測(cè)斌

1、開發(fā)周期及成本比較傳統(tǒng)的設(shè)計(jì)開發(fā)計(jì)算機(jī)工程 (CIE) 設(shè)計(jì)批量生產(chǎn)試制批量生產(chǎn)工程樣機(jī)累計(jì)成本工程樣機(jī)設(shè)計(jì)機(jī)械樣機(jī)調(diào)整試驗(yàn)?zāi)途梅治鰴C(jī)械樣機(jī)概念概念開發(fā)周期Slide 51疲勞分布圖Slide 6What is Metal Fatigue?Slide 4有限元疲勞分析的作用 nCode 2005 Slide 3基于有限元的虛擬疲勞 有限元疲勞分析的作用 多軸Dang Van疲勞分析 有限元疲勞分析過(guò)程 焊點(diǎn)疲勞分析 有限元疲勞分析輸入 焊縫疲勞分析 有限元分析及結(jié)果簡(jiǎn)介 振動(dòng)疲勞分析 有限元疲勞應(yīng)力應(yīng)變獲取 高溫疲勞分析 S-N疲勞分析 疲勞分析技術(shù) E-N疲勞分析 Duty Cycle 疲勞

2、分析Slide 2nCode 疲勞耐久性工程高級(jí)培訓(xùn)班課程基于有限元的虛擬疲勞 nCode 2005 Slide 12有限元疲勞分析的作用 早期對(duì)“虛擬零部件”或“虛擬樣機(jī)”的疲勞分析 優(yōu)化將能大大縮短的開發(fā)周期 評(píng)價(jià)當(dāng)前的樣機(jī) 也可用來(lái)與試驗(yàn)結(jié)果比較評(píng)價(jià)計(jì)算Slide 12Design Process DurabilitySlide 11疲勞耐久設(shè)計(jì)過(guò)程Slide 10分析優(yōu)化Slide 9疲勞分布圖Slide 8疲勞分布圖Slide 73載荷輸入 等幅載荷 變幅載荷Slide 18有限元疲勞分析輸入 nCode 2005 Slide 17常用的疲勞分析模型 Local S-N Critic

3、al plane method E-N (local strain approach) Dan Van multiaxial fatigue limit Low cycle multiaxial fatigue Seam weld fatigue Spot weld fatigue High temperature fatigue Slide 16有限元疲勞分析過(guò)程 根據(jù)載荷用有限元計(jì)算應(yīng)力應(yīng)變響應(yīng)，需要哪一種響應(yīng)取決于所采用的疲勞計(jì)算 由于載荷信號(hào)通常為較長(zhǎng)的時(shí)域信號(hào)，所以通常使用一些簡(jiǎn)化 ，節(jié)省應(yīng)力應(yīng)變響應(yīng)計(jì)算時(shí)間 對(duì)每個(gè)應(yīng)力應(yīng)變已知點(diǎn)使用疲勞 模型進(jìn)行疲勞 計(jì)算，獲取模型全場(chǎng)的分布Sli

4、de 15有限元疲勞分析流程圖Slide 14有限元疲勞分析過(guò)程 nCode 2005 Slide 134典型的有限元分析類型 靜態(tài)（力）分析 線彈性分析 動(dòng)態(tài)分析 彈塑性分析 直接瞬態(tài)法 模態(tài)疊加法 強(qiáng)迫振動(dòng) 隨機(jī)振動(dòng)分析（應(yīng)力功率譜密度計(jì)算）Slide 24有限元分析類型 nCode 2005 Slide 23材料性能輸入Slide 22幾何輸入Slide 21獲取載荷：實(shí)測(cè)加多體動(dòng)力學(xué)分析Slide 20怎樣獲取載荷？ 實(shí)測(cè)- using wheel force transducers, load cells and strain measurements from instrument

5、ed prototype 實(shí)測(cè)加分析模擬- using wheel forces and accelerations from prototype or from earlierSlide 19m(adjusted for weight etc) and calculating component forces using Multi-Body Simulation software such as ADAMS, or using measured strains to determine forces or moments分析模擬- using Multi-Body Simulation s

6、oftware, including tire ms, and knowing the road surface profile根據(jù)標(biāo)準(zhǔn)5模態(tài)疊加Slide 30有限元模態(tài)瞬態(tài)法動(dòng)應(yīng)力分析 結(jié)構(gòu)有動(dòng)力響應(yīng)，或者所施加的載荷頻率相對(duì)接近于結(jié)構(gòu)的自然頻率 Dynamics and degrees ofdom of system are reduced to a set of modes and therefore much quicker to solve than direct method. Requires an appropriate set of modes to be selected

7、. Restricted to linear problems (and commonly used) 輸入載荷為時(shí)間的函數(shù) 輸入材料常數(shù)E, 有限元分析為模態(tài)疊加法 輸出結(jié)果為應(yīng)力/應(yīng)變的時(shí)間函數(shù)Slide 29有限元直接積分瞬態(tài)法應(yīng)力分析 結(jié)構(gòu)有動(dòng)力響應(yīng)，或者所施加的載荷頻率相對(duì)接近于結(jié)構(gòu)的自然頻率 Equations of motion of the complete system must be integrated through each time step Time consu Enable non-linear dynamic problems to be solve 輸入載荷

8、為時(shí)間的函數(shù) 輸入材料常數(shù)E, 有限元分析為直接瞬態(tài)法， 輸出結(jié)果為應(yīng)力/應(yīng)變的時(shí)間函數(shù)這一計(jì)算量往往驚人，這給實(shí)際應(yīng)用帶來(lái)了一定的Slide 28靜力分析 Advantages: Computationally cheap for FE analysis. Minimizes disk space requirements. Enables same stress data to be used for different loading events for fatigue analysis. (ie multiple events) Auto-elimination can be use

9、d to select entities prior to fatigue analysis to speed up analysis. Disadvantages: Static FE analysis requires some kind of constraint which can be unrealistic. Insufficient accuracy where the natural frequencies of thesystem areto the frequency content of the loading.Slide 27有限元彈性或彈塑性時(shí)間分析 結(jié)構(gòu)沒(méi)有動(dòng)力響應(yīng)

10、 輸入載荷為路徑相關(guān) 輸入材料性能為E, 及單向應(yīng)力應(yīng)變拉伸曲線 輸出結(jié)果為時(shí)間步應(yīng)力/ 應(yīng)變Slide 26有限元彈性靜力分析 結(jié)構(gòu)沒(méi)有動(dòng)力響應(yīng)F=1 N 輸入載荷為常數(shù) 輸入材料常數(shù) E, 輸出結(jié)果為平衡態(tài)應(yīng)力/ 應(yīng)變Slide 256Studio Demo Display stress of piston (Node on element) in Studio to show the skin of shell elementSlide 36Nodes or Elements Selection should captureum stress For shell elements, us

11、ing element centroidal stresses is straightforward. Using corner or node at element requires some averaging to get a single tensor for each node For solid elements, element centroidal values are typically not adequate because they are distant from the surface. Alternatives are to skin the solid with

12、 shells and use the shell stresses or use the nodal stresses from FE code directly.Slide 35Uaged nodal stress at Top ShellSlide 34典型的有限元結(jié)果 應(yīng)力 (uaged) node on element averaged node on element at element centriod at integration points (ABAQUS) for shell element Top layer Bottom layer Top and BottomSli

13、de 33典型的有限元結(jié)果 應(yīng)力 溫度 應(yīng)變 塑性應(yīng)變 力(spot weld) 。結(jié)果依賴于單元類型，有限元等Slide 32有限元分析結(jié)果 nCode 2005 Slide 317Quiz 系統(tǒng)動(dòng)力響應(yīng)可以忽略，怎樣計(jì)算A 點(diǎn)應(yīng)力的應(yīng)力變化？Slide 42從有限元結(jié)果中直接獲取所需的應(yīng)力應(yīng)變3Slide 41從有限元結(jié)果中直接獲取所需的應(yīng)力應(yīng)變2Slide 40從有限元結(jié)果中直接獲取所需的應(yīng)力應(yīng)變1疲勞分析需要變化的應(yīng)力應(yīng)變Slide 39應(yīng)力應(yīng)變獲取 nCode 2005 Slide 38應(yīng)力應(yīng)變結(jié)果通常為Slide 378Answer B (Step 5) 疊加兩個(gè)應(yīng)力結(jié)果Slide

14、 48Answer B (Step 4) 把力作用下的應(yīng)力值作為縮放系數(shù)計(jì)算豎向載荷變化作用下A點(diǎn)的應(yīng)力變化歷程Slide 47Answer B (Step 3) 再施加橫向力 再用有限元進(jìn)行靜力分析得到A點(diǎn)的應(yīng)力Slide 46Answer B (Step 2) 把力作用下的應(yīng)力值作為縮放系數(shù)計(jì)算豎向載荷變化作用下A點(diǎn)的應(yīng)力變化歷程Slide 45Answer B (Step 1) 先施加豎向力 用有限元進(jìn)行靜力分析得到A點(diǎn)的應(yīng)力Slide 44Answer A 同時(shí)施加兩個(gè)方向的載荷，保持其相位 用有限元進(jìn)行時(shí)間分析 直接得到A點(diǎn)的時(shí)間步應(yīng)力Slide 439基于有限元結(jié)果的S-N分析法

15、nCode 2005 Slide 54有限元疲勞分析流程圖Slide 53模態(tài)疊加Slide 52有限元疲勞分析流程圖Slide 51準(zhǔn)靜態(tài)分分析 鑒別各個(gè)加載點(diǎn)和約束以模擬工作環(huán)境 實(shí)測(cè)或分析各個(gè)加載點(diǎn)的時(shí)域信號(hào) 對(duì)每個(gè)載荷工況進(jìn)行有限元靜力計(jì)算 對(duì)所有的工況進(jìn)行靜力疊加，其彈性應(yīng)力變化歷下式計(jì)算其中 k 為載荷工況這一適用于激勵(lì)載荷頻率遠(yuǎn)離所分析構(gòu)件的任何自然頻率！Slide 50準(zhǔn)靜態(tài)應(yīng)力疊加*Slide 4910局部應(yīng)名義應(yīng)力 在有限元疲勞分析中用名義應(yīng)力SN法，非常，名義應(yīng)力很難定義，Kf很難計(jì)算 相反，用局部應(yīng)非常容易，用Kt近似Kf，疲勞結(jié)果偏保守有限元SN法實(shí)際上是局部應(yīng)！Sl

16、ide 60S-N曲線缺口Slide 59應(yīng)力集中系數(shù)Slide 58S-N 曲線法思路 從試樣中測(cè)出材料的S-N 曲線 考慮實(shí)際零件和試樣的差別，S-N 曲線 考慮試驗(yàn)加載和實(shí)際加載的區(qū)別 應(yīng)用雨流技術(shù)對(duì)應(yīng)力信號(hào)進(jìn)行循環(huán)周計(jì)數(shù) 結(jié)合Miner 損傷累積法則計(jì)算疲勞S-N 曲線法(名義應(yīng)) 是以交變名義應(yīng)力為主要參量零部件疲勞失效循環(huán)的一種經(jīng)驗(yàn)。Slide 57S-N 曲線 (MANTEN)First fatigue strength exponent b1 = -0.2Stress Range Intercept SRI1=3162 MPaUltimate tensile strength

17、UTS=600 MPaFatigue transition PointNc1=2e8Second fatigue strength exponent b2=0R-ratio RR=-1Slide 56SN Fatigue Tests Specimens are subjected to constant amplitude loading The number of cycles to failure is plottedthe nominal elastic stress on a log-log plot and the best fit curve computed There are

18、standards Curves can be derived for smooth specimens, individual components, sub-assemblies or complete structuresSlide 5511關(guān)鍵面法 Calculate stress on the surface and resolve on to several radial planes. Rainflow count and calculate the fatigue damage on each plane The CRITICAL plane is the one with t

19、he most damage!Slide 66有限元SN法計(jì)算流程Slide 65疲勞計(jì)算需要正負(fù)號(hào)Slide 64常用等效應(yīng)力Slide 63有限元SN法中的應(yīng)力多軸性考慮 等效應(yīng) 關(guān)鍵面法Slide 62有限元SN法的應(yīng)力獲取 準(zhǔn)靜態(tài)應(yīng)力疊加 直接積分瞬態(tài)或模態(tài)瞬態(tài)動(dòng)力計(jì)算 時(shí)間步計(jì)算（考慮接觸等）Slide 6112應(yīng)變?cè)囼?yàn) Test carried out to ASTME606 High quality test specimen Polished surface Precision machined for minimum surface residual Stress Strai

20、n monitoring using high quality clip gaugeSlide 72基于有限元結(jié)果的e-N分析法 nCode 2005 Slide 71SN疲勞分析Slide 70SN疲勞分析Slide 69基于局部應(yīng)力的疲勞計(jì)算Slide 68應(yīng)力雙軸性評(píng)價(jià)Slide 6713Neubers Rule: Kf2Se = Slide 78名義應(yīng)變和局部應(yīng)變Slide 77應(yīng)力集中系數(shù)Slide 76e-N 曲線法思路Slide 75應(yīng)變曲線Slide 74循環(huán)應(yīng)力應(yīng)變和應(yīng)變曲線Slide 7314有限元eN法中的應(yīng)力多軸性考慮Slide 84Rainflow Counting:

21、 behaviourSlide 83Stress Strain TrackingSlide 82有限元e-N法的應(yīng)變獲取Slide 81Slide 80Slide 7915eN 疲勞分析Slide 90eN 疲勞分析Slide 89典型的基于局部應(yīng)變的疲勞計(jì)算Slide 88Summary of Critical Plane Approach Assume uniaxial and find critical locations Examine strain time histories at critical locations for anomalies Examine strain hi

22、stograms at critical locations Assess multiaxiality at critical locations by checking biaxiality ratio and angle of principal Ile constant and constant ae 0, use Hoffman- Seeger (or Parameter Modification) biaxiality correction and abs max principal Ile varies greatly with time, needs multiaxial If

23、ae varies greatly with time, needs multiaxialSlide 87關(guān)鍵面法Slide 86常用等效應(yīng)變Slide 8516Stabilized residual stresses: The stabilized local residual stresses are calculated by means of an iteration in which convergence assumes a stabilized state, a state of elastic shakedown. As the loading sequence is repe

24、ated the “yield surface” grows and move with a combination of kinematic and isotropic hardening until it stabilises The stabilised yield surface is a 9 dimensional hypersphere that encompasses the loading historySlide 96Dang Van CriterionSlide 95Dang-Van CriterionSlide 94Dang Van criterion The Dang

25、Van criterion is a fatigue limit criterion It is based on the premise that there is plasticity on a microscopic level, leading to shakedown After shakedown, the important factors for fatigue are the amplitude of the microscopic shear stresses and the magnitude of the hydrostatic stress The method ha

26、s a complicated way of estimating the residual stressSlide 93基于有限元的多軸Dang Van 疲勞分析法 nCode 2005 Slide 92eN 疲勞分析Slide 9117Dang Van 分析Slide 102Dang Van 分析Slide 101有限元Dang Van法的應(yīng)力獲取 準(zhǔn)靜態(tài)應(yīng)力疊加 直接積分瞬態(tài)或模態(tài)瞬態(tài)動(dòng)力計(jì)算！只需要彈性應(yīng)力Slide 100Stabilized residual stresses:Slide 99Dang-Van Criterion Summary Is a High-Cycle fa

27、tigue criterion (infinite fatigue life) Can deal with three-dimensional loading Can deal with general multiaxial loading Is constructed on the basis of microscopic level: the scale of one or a few grains Can identify the direction of crack initiationSlide 98Dang Van 結(jié)果圖Slide 9718焊點(diǎn)疲勞分析簡(jiǎn)介1 用殼單元模擬連接板

28、用有限元中的剛性梁?jiǎn)卧M焊核 用有限元求取通過(guò)梁?jiǎn)卧獋鬟f的力矩 根據(jù)這些 力矩用工程 計(jì)算焊核附近連接板和焊核周圍的“結(jié)構(gòu)應(yīng)力” 通過(guò)一組以結(jié)構(gòu)應(yīng)力為參數(shù)的焊點(diǎn)SN曲線估計(jì)焊點(diǎn)的疲勞損傷Slide 108工業(yè)界現(xiàn)在是如何處理點(diǎn)焊的？焊點(diǎn)的數(shù)目、位置和的確定主要根據(jù)： 以前的經(jīng)驗(yàn) 不考慮焊點(diǎn)時(shí)連接板的應(yīng)力 生產(chǎn)工藝的可能性及性Slide 107The spot weld a crack waiting to fail “the nugget can be considered as the remaining central ligament of a cracked solid” (Smit

29、h & Cooper)Weld “nugget”Slide 106為什么要對(duì)焊點(diǎn)進(jìn)行耐久分析？ 約50% 汽車結(jié)構(gòu)耐久問(wèn)題和焊點(diǎn)有關(guān) 約80% 汽車車體的耐久問(wèn)題和焊點(diǎn)有關(guān) 在一條自動(dòng)生產(chǎn)線上裝備一個(gè)焊點(diǎn)的點(diǎn)焊裝置約需30,000 以后再補(bǔ)加一個(gè)焊點(diǎn)的點(diǎn)焊裝置約需兩倍的費(fèi)用Slide 105汽車中的焊點(diǎn)Slide 104焊點(diǎn)疲勞分析 nCode 2005 Slide 10319焊點(diǎn)疲勞分析1 從有限元分析中計(jì)算焊點(diǎn)所傳遞的力矩Slide 114焊點(diǎn)疲勞材料性能曲線 對(duì)典型的焊點(diǎn)試件進(jìn)行疲勞試驗(yàn) 分別獲取焊核和母材金屬的S-N 曲線Slide 113載荷輸入 用有限元靜力計(jì)算和線性疊加法獲取通過(guò)

30、焊點(diǎn)傳遞的力矩隨時(shí)間的變化Slide 112點(diǎn)焊結(jié)構(gòu)的幾何模擬1 在有限元模型中用剛性梁?jiǎn)卧M焊點(diǎn)！Slide 111怎樣模擬焊點(diǎn)的疲勞？Slide 110焊點(diǎn)疲勞分析簡(jiǎn)介2 剛性梁周圍的網(wǎng)格不需要細(xì)化 用Miner 疲勞損傷累積處理變幅載荷 該來(lái)說(shuō)可應(yīng)用于多軸載荷情況Slide 10920使用經(jīng)驗(yàn) Spotweld 程序界面友好，使用容易 能找出會(huì)出問(wèn)題的焊點(diǎn) 如果用性的材料性能曲線，那么所以的會(huì)比較保守 用特定焊點(diǎn)S-N曲線所獲得的結(jié)果和試驗(yàn)結(jié)果有較關(guān)聯(lián)，能得到正確的失效焊點(diǎn)位置Slide 120焊點(diǎn)分析Slide 119焊點(diǎn)分析Slide 118Life Prediction of S

31、pot Welded StructuresSlide 117焊點(diǎn)疲勞分析3 根據(jù)S-N 曲線，對(duì)焊點(diǎn) 每隔10度，計(jì)算一個(gè)疲勞損傷值， 取其大值Slide 116焊點(diǎn)疲勞分析2Slide 11521薄板焊縫的疲勞問(wèn)題Slide 126焊接對(duì)結(jié)構(gòu)疲勞耐久的影響Weld toeParent plateFusion zoneHeat affected zone Seam weld in a tube,showing grain structureSlide 125焊縫開裂導(dǎo)致的結(jié)構(gòu)失效Slide 124焊縫的疲勞分析 nCode 2005 Slide 123進(jìn)一步的資料 工程焊點(diǎn)疲勞機(jī)械工程1998

32、 年11期35-38頁(yè)Slide 122焊點(diǎn)分析總結(jié) Spotweld 能用來(lái)預(yù)估焊點(diǎn)疲勞 系統(tǒng)主要基于德國(guó)LBFRupp，Storzel和Grubisic 等人的工作 具有良用戶界面，它能方便地幫助分析最短的焊點(diǎn)位置 當(dāng)前這一系統(tǒng)已經(jīng)用于汽車底盤、懸架系統(tǒng)以及車體的耐久分析，已取得良效果Slide 12122基于名義應(yīng)力或熱點(diǎn)應(yīng)力的零部件S-N nCode工具 GlyphWorks S-N GlyphWorks Signal DesignLife Virtual Strain Gauge DesignLife S-NSlide 132基于焊接標(biāo)準(zhǔn)的設(shè)計(jì)Slide 131基于焊接標(biāo)準(zhǔn)的設(shè)計(jì) 焊

33、接標(biāo)準(zhǔn)通?；诖罅康膶?shí)驗(yàn)總結(jié)，并加兩倍的應(yīng)力安全系數(shù) 英國(guó)標(biāo)準(zhǔn) BS7608 歐洲標(biāo)準(zhǔn)天津工程機(jī)械研究所做過(guò)一些數(shù)據(jù) 來(lái)說(shuō)，所給出的 S-N 曲線很保守 要準(zhǔn)確焊縫型式比較 nCode已英國(guó)標(biāo)準(zhǔn)Slide 130焊縫疲勞的一些 基于名義應(yīng)力的零部件 S-N 基于 “Structural” （熱點(diǎn)）應(yīng)力的 S-N 基于焊接設(shè)計(jì)規(guī)范 基于斷裂力學(xué)的疲勞裂紋擴(kuò)展 基于節(jié)點(diǎn)力的 S-N（焊點(diǎn)） 基于局部應(yīng)力或力的 S-N（焊縫）Slide 129焊縫的特點(diǎn) 焊縫材料不均勻，金相組織不均勻 焊縫處殘余應(yīng)力 焊縫處幾何不連續(xù)，較大的應(yīng)力集中 焊縫處經(jīng)常焊接缺陷 相對(duì)于母材，焊縫的疲勞分散性較大Slide

34、128厚板焊縫的疲勞問(wèn)題Slide 12723S t r e s s R a n g e ( M P a )Weld Types - OverlapSlide 138Weld Types - FilletSlide 137Volvo/Chalmers/nCode approach Designed and validated for thin sheet automotive structures (1-5 mm sheet thickness) Based on structural stress at weld toe, root and throat Generic weld damag

35、e curves Interpolation between bending and membrane behaviour for fillet welds Mean stress corrections Thickness correctionsSlide 136基于局部應(yīng)力或力的 S-N（焊縫）Slide 135基于應(yīng)力的 仔細(xì)選擇焊接測(cè)試件，進(jìn)行等 應(yīng)調(diào)查結(jié)果的分散性幅試驗(yàn)。受力形式， 焊接工藝， 焊縫型式應(yīng)當(dāng)和實(shí)際結(jié)構(gòu) 調(diào)查臨界損傷累積常數(shù)近似 設(shè)計(jì)時(shí)可取下限并適當(dāng)加安全 選擇合適的有代表性的應(yīng)力作系數(shù) 為計(jì)算應(yīng)力或應(yīng)變（應(yīng)力，局部應(yīng)力等） 定義適當(dāng)?shù)氖c(diǎn) 必要時(shí)，可用有限元對(duì)測(cè)試件

36、進(jìn)行分析獲取測(cè)試件的應(yīng)力應(yīng)變分布的取決于實(shí)際工件的應(yīng)力應(yīng)變分析精度以及試驗(yàn)精度Slide 134虛擬應(yīng)變計(jì)Slide 133S-N Data PlotclassFSRI1: 1.201E4 b1: -0.3333 b2: -0.2 E: 2.07E5 UTS: 500 BS4360-50DSRI1: 1903 b1: -0.123 b2: 0 E: 1.914E5 UTS: 4801E31E21E11E3 1E4 1E5 1E6 1E7 1E8Life (Cycles)24Weld End TreatmentRootTTRoot*T T TTT TTToe*All elements in fr

37、ont orweld areconsidered. Option to include elements marked with *Slide 144Ming of Seam Weld EndsSlide 143Volvo/Chalmers/nCode approach - Ming guidelines and calculation points should be meshed predominantly with 4-noded quadrilateral elements (CQUAD4 or equivalent) representing the mid-planes of th

38、e metal sheets. The weld bead should be represented by a single or double row of shells. The mesh around the weld should be regular, with elements of around 5mm in size, and triangular elements in the viciof the weld should be avoided. The elements representing the weld bead are used to identify the

39、 weld, and these elements must be placed in a unique property set for each weld or weldtype. In addition, the weld element normals must be aligned so that the normals point outwards, that is towards the welder (except for Laser Overlap welds). The orientation of the sheet element normals is not impo

40、rtant, except that within a single sheet they should be aligned in compliance with normal good practice. Uaged node-at-element stresses are recovered for the weld toes and weld roots, based upon the elements adjacent to the weld and used to make the fatigue calculations. Where weld throat calculatio

41、ns are, the centroid stress from the weld toe element is used (averaged from the nodes).Slide 142Weld Types - GenericSlide 141Weld Types - Laser edge overlapSlide 140Weld Types - Laser overlapSlide 13925Overlap weld calculation pointsSlide 150Fillet weld calculation pointsSlide 149Weld fatigue locat

42、ions Weld elements used to locate adjacent elements used for the fatigue calculation Locations include the weld toe, weld root, and weld throat Weld fatigue locationivated by assigning them material propertiesSlide 148Laser overlap weldSlide 147Overlap and laser edge overlap weldsSlide 146Fillet weld mingSlide 145