教程其他也可參考差別不大曲軸機(jī)構(gòu)仿真

GT-SUITE曲軸機(jī)構(gòu)分析李書澤所屬：CDAJ-China目錄曲軸系分析功能簡(jiǎn)介1.曲軸系剛體動(dòng)力學(xué)2.發(fā)動(dòng)機(jī)平衡不平衡力/力矩3.

機(jī)體振動(dòng)

–

懸置分析與設(shè)計(jì)4.曲軸扭振5.軸承油膜分析6.曲軸柔性(彎曲)模型7.曲軸應(yīng)力恢復(fù)與后處理選項(xiàng)8.校核Copyright

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Reserved.1曲軸系分析目的:多缸機(jī)中振動(dòng)、動(dòng)力學(xué)、摩擦學(xué)仿真缸內(nèi)壓力和往復(fù)慣性力對(duì)曲軸系部件結(jié)構(gòu)的影響。GT-SUITE工具:通用多體動(dòng)力學(xué)庫(kù)曲軸設(shè)計(jì)分析庫(kù)Copyright

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Reserved.2GT-SUITE的曲軸系設(shè)計(jì)分析功能Copyright

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Reserved.3曲軸動(dòng)力學(xué)分析曲軸系剛性Rigid運(yùn)動(dòng)學(xué)和動(dòng)力學(xué)曲軸扭振Torsional(時(shí)域+頻域)曲軸3D彈性elastic分析:扭轉(zhuǎn)+彎曲,與軸承油膜耦合(動(dòng)力學(xué)或準(zhǔn)靜力學(xué)),應(yīng)力恢復(fù)&疲勞后處理其他功能平衡–

不平衡力/力矩，平衡軸機(jī)體振動(dòng)

- 懸置分析設(shè)計(jì)曲軸連桿軸承油膜分析與GT-SUITE其他模塊的集成仿真曲軸動(dòng)力學(xué)分析剛性Rigid, 平衡扭振Torsional (頻域或時(shí)域)彎曲Bend(3D梁有限元)Copyright

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Reserved.4其他曲軸系分析計(jì)算缸體+懸置動(dòng)力學(xué)主軸、連桿軸承Copyright

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Reserved.5與發(fā)動(dòng)機(jī)、車輛、其余子系統(tǒng)集成發(fā)動(dòng)機(jī)，燃燒模型

(GT-POWER)氣閥/凸輪軸車身與動(dòng)力總成Copyright

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Reserved.7四缸機(jī)曲軸系模型曲軸部件組成軸承油膜曲軸分析控制缸壓活塞連桿缸體懸置，底盤Copyright

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Reserved.92-或4-沖程任意的氣缸布置型式(直列,V,W,Box等.)單，雙或者開口銷曲拐V型發(fā)動(dòng)機(jī)左或右手交替考慮活塞銷，曲柄和連桿軸向偏心每個(gè)氣缸可單獨(dú)設(shè)置屬性(缸壓曲線，活塞，連桿，曲軸等)靈活的氣缸編號(hào)規(guī)則缸壓曲線隨轉(zhuǎn)速而變，或者由IMEP產(chǎn)生穩(wěn)態(tài)或瞬態(tài)分析預(yù)定義的曲軸轉(zhuǎn)速,或者在預(yù)定義負(fù)荷下的自由加速GT-SUITE進(jìn)行曲軸系設(shè)計(jì)分析的優(yōu)勢(shì)Copyright

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Reserved.10所有的分析功能及模式在單一軟件內(nèi)完成廣泛的適應(yīng)性，完全的通用性快速,易用,優(yōu)化功能附帶GT-SUITE

通用工具DOE,

Optimizer,

Dist.

Run,

NN,

Controls等與其他GT-SUITE模塊易于集成GT-POWER:燃燒計(jì)算配氣機(jī)構(gòu)，凸輪軸齒輪、鏈和帶傳動(dòng)液壓、潤(rùn)滑和軸承(曲軸系分析功能簡(jiǎn)介-結(jié)束)Copyright

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Reserved.111.曲軸系剛體動(dòng)力學(xué)活塞，曲柄銷及軸承受力曲軸內(nèi)應(yīng)力及發(fā)動(dòng)機(jī)扭矩軸承油膜及質(zhì)心軌跡計(jì)算Copyright

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Reserved.12“合成”的缸壓曲線Copyright

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Reserved.13可以根據(jù)用戶的輸入合成隨曲軸轉(zhuǎn)角變化的缸壓曲線:IMEP進(jìn)排氣壓力燃燒燃燒始點(diǎn)，持續(xù)期對(duì)于概念研究，還沒(méi)有缸壓曲線時(shí)特別有用，也適用于瞬態(tài)模擬。2.發(fā)動(dòng)機(jī)平衡不平衡力/力矩Copyright

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Reserved.14不平衡力矩(發(fā)動(dòng)機(jī)反作用扭矩,Mz)不平衡(搖晃)力和力矩-Fx,

Fy,

Mx,

My活塞、連桿往復(fù)慣性力及力矩帶一或多平衡重的平衡軸不平衡力、力矩、扭矩階次分析精確求解(包含高階諧次，無(wú)近似)自動(dòng)“端腹板e(cuò)nd

web”平衡特性

–

自動(dòng)計(jì)算質(zhì)心位置平衡一階不平衡力矩四缸機(jī)-不平衡力/力矩Copyright

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Reserved.16FyFzMxMyMz四缸機(jī)-不平衡力/力矩階次分析缸體彎矩-Mx輸出缸體瞬時(shí)彎矩和整體最大彎矩(Mx,My)評(píng)價(jià)缸體載荷設(shè)定設(shè)計(jì)標(biāo)準(zhǔn)缸體彎矩隨著軸向位置和曲軸轉(zhuǎn)角的變化缸體彎矩隨著軸向位置的變化(在最大彎矩角度)Copyright

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Reserved.17輸出機(jī)體所有受力情況輸出間隔1°曲軸轉(zhuǎn)角的，從所有軸承、氣缸傳遞給機(jī)體的力，包括活塞受側(cè)向力時(shí)的軸向坐標(biāo)，以表格型式給出?？捎糜诎l(fā)動(dòng)機(jī)機(jī)體的有限元NVH計(jì)算Copyright

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Reserved.18帶雙平衡軸的四缸直列機(jī)曲軸系平衡軸平衡軸齒輪使用GT-SUITE

OPTIMIZER計(jì)算的平衡重Copyright

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機(jī)體振動(dòng)

–

懸置分析與設(shè)計(jì)Copyright

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Reserved.20懸置位置坐標(biāo)(坐標(biāo)系，懸置裝配方向)在本地坐標(biāo)系下的懸置剛度、阻尼特性作為受懸置約束以及受不平衡力及力矩作為激勵(lì)的剛體慣量的缸體-傳動(dòng)系機(jī)體6自由度運(yùn)動(dòng)，質(zhì)心、支承點(diǎn)(或任意點(diǎn))運(yùn)動(dòng)及受力發(fā)動(dòng)機(jī)+路面激勵(lì)對(duì)懸置作用力缸體運(yùn)動(dòng)(模態(tài))頻域特性和模態(tài)圖4缸直列機(jī)－曲軸、機(jī)體和缸體模型懸置底盤Copyright

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Reserved.21四缸機(jī)-5000

RPM支承位移壓力+慣性力Mount2Mount1Mount3Mount4Initial

settling

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Reserved.23Mount1Mount3Mount4壓力+慣性力懸置系統(tǒng)模態(tài)頻率和振形圖Copyright

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Reserved.25曲軸扭轉(zhuǎn)慣量/剛度建模時(shí)域扭振分析頻域(FD)扭振分析自由振動(dòng)分析(自然頻率和模態(tài)圖)受迫振動(dòng)頻響分析外部部件耦合到曲軸,包括另外的軸系部件,驅(qū)動(dòng)軸系,齒輪系等可以耦合到模型中，(時(shí)域或頻域分析)也可以包含其他的子系統(tǒng)粘彈性橡膠阻尼模型曲軸扭振建模Copyright

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Reserved.26扭轉(zhuǎn)曲軸慣量:每個(gè)主軸頸,曲柄臂,曲柄銷定義一個(gè)位于各自中心的慣量根據(jù)幾何及材料密度自動(dòng)計(jì)算部件慣量，但用戶可以通過(guò)輸入慣量作出修正剛度:

扭轉(zhuǎn)剛度根據(jù)材料屬性及等效長(zhǎng)度計(jì)算+按BICERA推薦算法計(jì)算的曲柄臂等效剛度/長(zhǎng)度可以選用用戶自定義剛度阻尼:材料(遲滯)阻尼比外部阻尼(摩擦)曲軸扭振模型飛輪慣量軸頸慣量曲柄銷慣量曲柄臂慣量附加轉(zhuǎn)動(dòng)慣量集中慣量扭轉(zhuǎn)柔度+材料阻尼Copyright

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Reserved.29輸入剛度(軸頸中心到曲柄銷中心距),或BICERA方法*:等效長(zhǎng)度(EL)從實(shí)驗(yàn)數(shù)據(jù)查參數(shù)化曲柄臂模型得到等效長(zhǎng)度“矩形化”曲柄臂vs.基本曲柄臂尺寸比查表EL(曲柄半徑,曲柄臂厚,軸頸直徑,曲柄臂寬)根據(jù)最大軸頸/銷直徑超過(guò)臂寬修正根據(jù)曲柄銷與軸頸直徑比與重疊的修正可選項(xiàng)(曲柄臂幾何對(duì)象):對(duì)軸頸和曲柄銷孔徑,銷的偏心距修正軸頸、曲柄臂與曲柄銷連接部圓角修正曲柄臂切口修正*

The

British

Internal

Combustion

Engine

Research

Association,

A

Handbook

of

Torsional

Vibrations,

E.J

Nestorides,

Ed.

(1958)曲柄臂扭轉(zhuǎn)變形參數(shù)Copyright

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Reserved.31通過(guò)與運(yùn)動(dòng)方程聯(lián)合求解所有自由度的扭振自動(dòng)調(diào)整計(jì)算步長(zhǎng)，雙精度求解，允許長(zhǎng)時(shí)間瞬時(shí)計(jì)算穩(wěn)態(tài)分析，預(yù)定義的車速變化的瞬態(tài)或根據(jù)負(fù)載加速的瞬態(tài)分析，允許發(fā)動(dòng)機(jī)轉(zhuǎn)速變化其余的部件模型與剛性分析(不平衡力,平衡軸,軸承缸體振動(dòng)和支承)相同曲軸扭振–時(shí)域仿真II角位移、角速度、角加速度局部應(yīng)力，扭轉(zhuǎn)變形曲拐角變形(傳遞誤差)中間扭矩,曲軸扭矩工作應(yīng)力(扭轉(zhuǎn)應(yīng)力+橫向剪切應(yīng)力,彎曲應(yīng)力)隨時(shí)間變化，平均值，最大、最小值，幅值時(shí)域得到的結(jié)果進(jìn)行頻域分析Copyright

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Reserved.曲軸扭振–

時(shí)域計(jì)算Angle

Shifts

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VelocityTorque

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頻域分析ICopyright

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Reserved.35快速線性分析(只需幾秒鐘)分支系統(tǒng)(例如發(fā)動(dòng)機(jī)與傳動(dòng)系)非線性，頻率相關(guān)的剛度、阻尼自由振動(dòng)分析扭振模態(tài)頻率(表格)模態(tài)圖受迫振動(dòng)分析自動(dòng)發(fā)動(dòng)機(jī)轉(zhuǎn)速掃描,考慮可變缸內(nèi)壓力激振力（單獨(dú)或插值），也可加上隨轉(zhuǎn)速變化的外部扭轉(zhuǎn)力矩自動(dòng)偵測(cè)共振轉(zhuǎn)速曲軸扭振–

頻域分析IICopyright

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Reserved.36受迫振動(dòng)分析(接前)隨發(fā)動(dòng)機(jī)轉(zhuǎn)速變化的曲柄銷處各諧次扭矩圖幅值響應(yīng)圖（各諧次角度,角速度,角加速度,扭矩,扭轉(zhuǎn)剪切應(yīng)力等）.基于階次/頻率、轉(zhuǎn)速的等高線圖時(shí)域圖參數(shù)提取:瞬時(shí)角度,角速度,角加速度,扭矩,可以輸入速度和隨時(shí)間變化或者頻率相關(guān)的扭矩激勵(lì)不規(guī)則轉(zhuǎn)速循環(huán)扭振阻尼功率瞬時(shí)計(jì)算自由頻域扭振–前4個(gè)模態(tài)Copyright

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Reserved.37受迫頻域扭振–受迫頻率分析對(duì)象(ForcedFreqAnalysis模板)Main:選擇轉(zhuǎn)速和步長(zhǎng)ORDER

PLOTS

vs.RPM:選擇節(jié)點(diǎn)和響應(yīng)階次作圖選項(xiàng):選擇節(jié)點(diǎn)頻率或階次頻率或階次選擇XY軸Copyright

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Reserved.38受迫頻率分析對(duì)象輸出及后處理Copyright

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Reserved.39受迫頻域扭振扭振分析–

對(duì)轉(zhuǎn)速的諧次響應(yīng)作圖Copyright

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Reserved.40強(qiáng)制頻率扭振分析–階次/頻率、轉(zhuǎn)速云圖VS

ORDER

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FREQUENCY

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CYLINDER2nd

Nat.

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Reserved.43Speed橡膠阻尼器建模橡膠阻尼采用Maxwell-Reichart型Solid模模型假定剛度、阻尼是頻率的函數(shù)

(Keff(f),Ceff

(f), -

函數(shù)關(guān)系由試驗(yàn)測(cè)得)

，Maxwell

模型的剛度和阻尼參數(shù)

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通過(guò)最小方差方法自動(dòng)擬合時(shí)域頻域物理描述是一致Copyright

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k1

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Reserved.45與試驗(yàn)數(shù)據(jù)的擬合Keff,Ceff:試驗(yàn)數(shù)據(jù)vs.最小方差擬合結(jié)果對(duì)比Keff

(f)Keff

(f)Ceff

(f)Copyright

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(f)Φeff

(f)

(Phase

or

loss

angle)Φeff

(f)

(Phase

or

loss

angle)Data

Set

1Data

Set

2Co(pyrPigh=t

(0C)

,2011

CPD-a=dapc0o

J.APA5N

CPo.,mLTDa.

Axll

,RighPts=RePsermveda.475.軸承油膜分析遷移率Mobility或者阻抗法Impedance

MethodMobility

and

Impedance兩種方法互為鏡像Mobility用于剛性，扭轉(zhuǎn)或準(zhǔn)靜力學(xué)彎曲曲軸動(dòng)力學(xué)的主軸承（即軸承反力已知）和連桿軸承Impedance狀態(tài)已知,用于主軸承的全動(dòng)力學(xué)求解求解反作用力)(軸頸詳細(xì)油膜輸出軌跡，最小油膜厚度最大壓力及其位置流率(液壓動(dòng)力學(xué),Martin,Martin-Xu等模型)油膜范圍 x

lines)Copyright

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Reserved.Mobility方法輸出

(Using

Fits

of

Goenka,1984)Mobility48Max.Pres.

LocationMax

PressureFilm

ExtentCopyright

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第二主軸承,

5000

RPM49Copyright

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Reserved.Mobility

方法求解四缸機(jī)–第二主軸承,5000

RPM50詳細(xì)油膜展開/壓力圖

(軸承，軸頸，連桿系統(tǒng))油膜展開圖——曲軸轉(zhuǎn)角(水平軸.)軸承圓周(垂直軸.)云圖油壓進(jìn)行了歸格化處理?；疑糠直硎?80°油槽GROOVECopyright

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(1958)方法的對(duì)比Copyright

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Film

Thickness

Maximum

Oil

PressureOil

Volume

FlowRateAttitude

AngleConrod

Large

End方法與其他工具的對(duì)比TOOL

ATOOL

CCopyright

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Tool

A方法的對(duì)比:三缸機(jī)主軸承載荷GT-SUITECopyright

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A與“In-house”

Tool

A方法的對(duì)比:三缸機(jī)主軸承質(zhì)心軌跡6.曲軸3-D彈性(彎曲)模型Copyright

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Reserved.573-D梁有限元分析提供兩種分析方式:準(zhǔn)靜力學(xué)動(dòng)力學(xué)動(dòng)力學(xué)模式下，線性彈性變形疊加到大的

3D剛體運(yùn)動(dòng)上準(zhǔn)靜力學(xué)模式下,線性化彈性位移根據(jù)相當(dāng)配置得出3-D

梁有限元方程Copyright

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Reserved.58生成線性化質(zhì)量和剛度矩陣2、3、4節(jié)點(diǎn)有限元全積分生成質(zhì)量矩陣降解積分生成剛度矩陣基于比例生成阻尼矩陣質(zhì)量、剛度和阻尼線性化高效skyline矩陣式存儲(chǔ)(稀疏矩陣)Cuthill-McKee

帶寬優(yōu)化算法動(dòng)力學(xué)計(jì)算中考慮小尺度旋轉(zhuǎn)和大位移在梁的任意位置進(jìn)行應(yīng)力計(jì)算(軸向和剪切應(yīng)力，彎曲和扭曲力矩)，使用簡(jiǎn)化積分算法梁節(jié)點(diǎn)可以指定速度梁剛體慣性負(fù)荷采用準(zhǔn)靜力學(xué)方程梁的有限元圖2,3,或4節(jié)點(diǎn)有限元方法可用于各種結(jié)構(gòu)如軸頸、曲柄臂、曲柄銷的建模Copyright

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Reserved.60表示曲拐的等效梁的截面（面積）力矩可以根據(jù)半曲拐已知的柔度（角度與偏斜）:作用在在曲軸銷中心，曲拐平面內(nèi)的力矩作用在曲軸銷中心，垂直于曲拐平面作用在曲軸銷中心的扭矩用戶可以通過(guò)FEA軟件或者試驗(yàn)得到上述柔度，作為GT-SUITE的輸入等效3D

Beam

FE

模型ElementsNodes3D曲柄臂固體FE模型柔度用于自動(dòng)創(chuàng)建當(dāng)量的3D梁FE模型Compliance

for

3

load

cases3D

FE

AnalysisCopyright

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pin)過(guò)度盤當(dāng)量梁屬性ElementsNodes3D

FE

分析3D

Load

Case

CompliancesCopyright

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Reserved.62臨界最大末端載荷－演示曲軸末端可以承受的最大載荷（例如驅(qū)動(dòng)其他裝置的齒輪或者鏈輪載荷）可以輸入載荷方向角，要滿足多項(xiàng)（軸承最小油膜厚度/最大壓力，曲柄/EFR應(yīng)力）要求（安全系數(shù)）GT-SUITE的Optimizer可以進(jìn)行快速，自動(dòng)計(jì)算Copyright

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Reserved.63曲軸彎曲的動(dòng)畫(變形放大100倍）注意每次TDC點(diǎn)火是峰值壓力的影響TDCBDCYCopyright

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[N-m]7.曲軸應(yīng)力恢復(fù)與后處理選項(xiàng)基本的3D梁?jiǎn)卧敵?，即，恢?fù)的剪切，力矩，扭矩，應(yīng)變

(隨時(shí)間變化,平均值,最小值,最大值，幅值)主軸和曲軸銷倒角的應(yīng)力集中基于用戶定義的應(yīng)力/彎矩比可選疲勞壽命計(jì)算主軸和曲軸銷倒角的應(yīng)力集中

(IACS

M53)船用發(fā)動(dòng)機(jī)曲軸認(rèn)證通過(guò)/不通過(guò)的標(biāo)準(zhǔn)基于彎曲和扭轉(zhuǎn)載荷的合力)EFRMEAN

TFSs

AMPss

=(1

-

sCopyright

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Reserved.663D固體FE應(yīng)力恢復(fù)與后處理(與單位載荷應(yīng)力場(chǎng)合成）作用在曲拐上（臨近主軸之間）準(zhǔn)靜力學(xué)或者動(dòng)力學(xué)計(jì)算得到了曲拐慣性系中外部載荷，剪應(yīng)力，彎矩通過(guò)與3D固體FE模型（靜態(tài)單位載荷）計(jì)算的應(yīng)力場(chǎng)疊加合成對(duì)于選定的曲拐和選定的角度輸出3-D

FE應(yīng)力使用強(qiáng)度數(shù)據(jù)和疲勞分析&Goodman圖（EFR應(yīng)力疲勞法）對(duì)于曲拐外載荷產(chǎn)生簡(jiǎn)單的列－格式化ASCII文件，可以為第三方疲勞分析軟件所用EFR

Stress/Fatigue

Methodology

IUnit

Load

Case

Detailed

3D

FE

AnalysisForces/Moments

from

CranktrainDesign

Analysis單位載荷3D-FEA節(jié)點(diǎn)應(yīng)力，乘以曲軸分析（梁有限元求解）得到的曲拐力和力矩，再線性疊加σi,j,k,m,s=

ΣnFk,nC

σ

n

i,j,m,sCopyright

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=

stress

factor(nodal

stress

for

unit

loadFn)Fn

=Instantaneous

forceormomentn=

unit

load

case

indexi=

stress

tensor

indexj=

FEnode

indexk=

crank

angle

(step)

indexm=

stress

concentration

zone

indexs

= solution

(crankthrow)indexC

F根據(jù)應(yīng)力和強(qiáng)度不同進(jìn)行可靠性計(jì)算EFR

Stress/Fatigue

Methodology

IIσ

EFR,ma

,m,s=

maxi

(σEFR,j,m,s)σ

EFR,max,s=

maxm

(σEFR,max,m,s)σ

EFR,max

=

maxj(σEFR,max,,s)σEFR,j,m,s

=

σamp,j,m,s/(1-

σmean,j,m,s/

σtfs)曲拐和曲軸，應(yīng)力集中區(qū)中最大EFR應(yīng)力EFR(Equivalent

Fully-Reversed)StressSPS和應(yīng)力矢量的循環(huán)最大，最小，平均和幅值

Von

Mises“amplitude”stress*主應(yīng)力篩選(SPS)σj,k,m,s單位載荷應(yīng)力疊加(瞬態(tài)應(yīng)力矢量)σi,j,k,m,s=

ΣnFk,nC

σn

i,j,m,sEFRCopyright

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Reserved.68A

=

1-UREFR*

“Von

Mises”

Stress

based

on

stress

cyclic

amplitude

tensorσ

max,j,m,s=

maxk(σj,k,m,s)σ

min,j,m,s=

mink(σj,k,m.s

)σ

mean,j,m,s=avgk(σj,k,m,s

)σ

amp,j,m,s

=

(σmax,j,m,s-

σmin,j,m,s)/2參考.對(duì)象自動(dòng)化過(guò)程ShaftStressAnalysis:

Master

Reference

ObjectShaftStressConcZones:

FE

Node

data

&

CS

Zone

DefinitionCrankUnitLoadcases:

Unitload

case

FEA

output

filesCopyright

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Reserved.69Pin

fillet

1LighteningpocketsCourtesy

of

Cummins,

Inc.Pin

fillet

2Oil

holeMain

Fillet

1Main

Fillet

2EFR

Stress/Fatigue

Methodology

IIICopyright

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Reserved.70多應(yīng)力集中區(qū)分別輸出的EFR應(yīng)力，疲勞可靠性8.校核6

Cylinder

In-line

CranktrainCopyright

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Orbits

–

Comparison

to

Tool

BTool

BCopyright

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BTool

BTool

BTool

BTool

BTool

BBearing

Loads

–

Comparison

to

Tool

BTool

BCopyright

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BTool

BTool

BTool

BTool

BTool

BComparisons

to

Tool

B(Bearings

-

Differences

in

%)BearingLoadMin.

Oil

FilmThicknessMax.OilPressureBearing

1-1.03-1.431.14Bearing

21.751.790.2Bearing

31.051.18-1.63Bearing

40.059-0.251.27Bearing

50.721.09-1.73Bearing

61.732.113.51Bearing

7-1.87-2.651.27Copyright

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to

In-house

Tool(Fillet

EFR

Stress

-

Differences

in

%)Crankpin

FilletJournal

FilletWeb

1L-1.94-0.98Web

1R-4.69-3.81Web

2L-3.04-2.48Web

2R-4.01-3.21Web

3L-3.48-2.81Web

3R-0.78-0.93Web

4L-1.74-0.85Web

4R-1.91-1.94Web

5L-2.98-2.43Web

5R-1.91-1.37Web

6L-4.66-3.45Web

6R-0.95-0.93Copyright

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filletBackJournalFilletComparison

to

In-house

ToolEFR

Stress

&

Acceptability四個(gè)應(yīng)力集中區(qū)Front

JournalFilletFrontPin

filletFRONTJOURNALFILLETBACKJOURNAL

FILLETFRONTPINFILLETBACKPINFILLET%

Diff%

Diff%

Diff%

DiffMax.

Component

Stress0.860.380.800.48EFR

Stress

–SPS

Method0.480.430.600.44EFR

Stress

–VMS

Method0.450.400.300.26Unreliability-SPS

Method8.418.129.655.19Copyright

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Engine

ValidationCopyright

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Comparison

to

Tool

BV8Loa-d4s

0–

0T

0

rBp,

–mMaximum

Bearing

Force070000600005000040000300002000010000152

3

4Main

Bearing

NumberForce

(N)Cummins#1#2#3#4#5GTTool

BCopyright

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Comparison

to

Tool

BV8

-

4000

rpmMinimum

Oil

Film

Thickness1.00.50.02.52.01.53.0152

3

4Main

Bearing

NumberMOFT

(mm)Cummins主軸承軌跡–Tool

B,–GT-SUITE#1#2#3#4#5GTTool

BCopyright

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Comparison

to

Tool

Bv8

-

4000

rpmPeak

Oil

Film

Pressure200180160140120100806040200152

3

4Main

Bearing

Num

berPOFP

(Mpa)CumminsGTTool

BPeak

OilFilm

Pressure

Difference-1-24321012345Main

BearingNumberPOFP

Difference(%)峰值油膜壓力Copyright

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Comparison

to

Tool

Bv8

-

4000

rpmMainFillets

Stress0400350300250200150100501236784

5Web

#Stress

(Mpa)CumminsGTTool

BPin

Fillets

Stress3503002502001501005001236784

5Web

#Stress

(Mpa)CumminsGTTool

BFillets

EFR

StressCopyright

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M53標(biāo)準(zhǔn)分析船舶應(yīng)用校準(zhǔn)根據(jù)IACS的標(biāo)準(zhǔn)計(jì)算曲軸強(qiáng)度，評(píng)估疲勞安全性基于的假定是：曲軸銷和曲柄臂間，主軸和曲柄臂間是最大應(yīng)力區(qū)對(duì)曲軸系統(tǒng)中的每個(gè)曲柄臂都進(jìn)行分析Copyright

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集成仿真(和其他GT-SUITE產(chǎn)品)Copyright

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Reserved.83配氣機(jī)構(gòu)和正時(shí)系統(tǒng)對(duì)于配氣機(jī)構(gòu)的動(dòng)力學(xué)影響與凸輪軸扭轉(zhuǎn)振動(dòng)的相互作用與齒輪、鏈或帶傳動(dòng)動(dòng)力學(xué)相互作用發(fā)動(dòng)機(jī)性能氣缸熱動(dòng)力學(xué)的相互作用失火的影響，失火檢測(cè)燃燒變動(dòng)缸間差異發(fā)動(dòng)機(jī)瞬態(tài)針對(duì)容積效率優(yōu)化點(diǎn)火順序而不影響扭轉(zhuǎn)動(dòng)力性車輛與傳動(dòng)系扭轉(zhuǎn)阻尼（隔振）分析與設(shè)計(jì)對(duì)驅(qū)動(dòng)系零件以及扭轉(zhuǎn)動(dòng)力學(xué)或者缸體3D振動(dòng)對(duì)支承的影響，特別是瞬態(tài)情況下GT-SUITE集成仿真:

Cranktrain+ValvetrainCopyright

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Reserved.84項(xiàng)目類型為“GT-SUITE”

,模擬曲軸，配氣機(jī)構(gòu)和其相互作用使用一個(gè)模型進(jìn)行曲軸和配氣機(jī)構(gòu)設(shè)計(jì)和相互作用分析更加準(zhǔn)確的捕捉下述特性：曲軸速度曲軸和配氣機(jī)構(gòu)扭轉(zhuǎn)動(dòng)力學(xué)相互作用齒輪系和鏈傳動(dòng)系的影響