Research Article Optimum Design for Mechanical Structures...

Research ArticleOptimum Design for Mechanical Structures and MaterialProperties of the Dual-Elbow-Bar Mechanism

Weiguo Lin Chen Zhou and Weijun Huang

College of Engineering Huazhong Agricultural University Wuhan 430070 China

Correspondence should be addressed to Weiguo Lin linweiguomailhzaueducn

Received 14 August 2014 Accepted 8 October 2014

Academic Editor Yan Yang

Copyright copy 2015 Weiguo Lin et al This is an open access article distributed under the Creative Commons Attribution Licensewhich permits unrestricted use distribution and reproduction in any medium provided the original work is properly cited

According to the kinematic equation of the die-cuttingmachinewith the dual-elbow-barmechanism the angular acceleration curvefigure can be obtained exactly through the analysis of MATLAB program when the die-cutting machine runs at the highest speed(6000 rh) The material properties of the cam driving mechanism are analyzed by QFD (Quality Function Deployment) methodand the optimum design project is presented based on conjugate cam driving mechanism The reverse design and the outline ofconjugate cam mechanism are obtained by MATLAB program The kinematical form of optimized design conjugate cam drivingmechanism is simulated and analyzed by ADAMS software The results show that the optimum design mechanism could raise thehighest speed of the die-cutting machine up to 7500 rh and improve the overall performance of the machine

1 Introduction

In printing and packaging machinery the dual-elbow-bardriving mechanism is the most important and essential partof die-cutting machine Its motion and force conditionsdirectly affect the precision of die-cutting the speed ofcutting and the machinersquos stability and reliability thereforethe kinematics and dynamics analysis of the dual-elbow-barmechanism is crucial [1]

In the hope of solving the existing problems of dual-elbow-bar mechanism many scholars had carried out studiesfrom the perspective of kinematics dynamics and the perfor-mance of the optimal design and some hadmade remarkableachievement Xie and Zou presented a method to analyze thedynamic response of the platen die-cutter which combinedthe finite element analysis of the die-cutting force andthe dynamic simulation of the dual-elbow-bar mechanismMeanwhile the analysis made it possible to calculate theutmost speed and the utmost cutting force of platen die-cutter[2] Li and Cheng solved the analytic equation about motion-stand ratio of double-bar chains die plate stroke and bardimension on the basis of a simplified model that overlookedminor factor [3] Zhang et al analyzed the motion of thedual-elbow-bar mechanism based on the loop method [4]

Yong et al introduced the method of conversion mechanismto solve the dual-elbow-bar groupmovement and consideredthat the senior bar group reduced to lower rod group whichreduces the computational complexity of motion analysis [5]Cheng andWang analyzed and calculated the reliability of theelbow-bar mechanism of automatic die-cutting machine bytaking the original errors as stochastic variables [6] Yanbin etal analyzed elbow-bar framework of the die-cutting systemofblocking die-cutter with numerical method and designed anexperiment to verify the mechanism property of die-cuttingsystem [7] Qun and Zhimin modeled and emulated thedual-elbow-bar mechanism of the die-cutting machine usingSolidWorks and analyzed the movement characters of somecomponent [8] Zhao and Li built the simulation model ofthe dual-elbow-bar mechanism of die-cutting machine basedon ADAMS which performed a simulation analysis on dual-elbow-bar mechanism and worked out the motion law of thedual-elbow-bar mechanism [9] Fan and Ding described theshiftlessness of the high-speed rotary die-cutting machineand its control system by comparing various transmissionand analyses of certain programs [10]

According to the existing research there are still somedeficiencies in design of die-cutting machine The causeof this situation is as follows (1) It mainly relies on the

Hindawi Publishing CorporationAdvances in Materials Science and EngineeringVolume 2015 Article ID 724171 5 pageshttpdxdoiorg1011552015724171

2 Advances in Materials Science and Engineering

A

Bo

C

D

F

A998400

E998400

B998400

D998400

C998400

l1

l8

l2

l5

l3

l4

l9

1205795

1205791

1205792

1205793

1205794

s

2l7

120579998400

3

120579998400

1

120579998400

2

120579998400

4

l998400

9

l998400

2

l998400

4

l998400

3

l998400

5

l998400

1

Figure 1 The dual-elbow-bar driving mechanism of die-cuttingmachine

traditional design method which causes low processing effi-ciency production quality and accuracy and poor stability(2)Material selection is dependent on experience lacking ofguidance on using the QFD tool (3)The virtual simulationtechnology of optimization design method in the design ofdie-cutting machine is still not mature

The main die-cutting mechanism of die-cutting machinediagram is a ten-bar mechanism which is complex andsymmetrical as showed in Figure 1 In Figure 1 AA1015840 is thedriving crank AB and A1015840B1015840 are the connecting rods BCand B1015840C1015840 are the lower toggle rods BD and B1015840D1015840 are theupper toggle rods and DD1015840 is the cutting platform Sincethe mechanism is symmetrical from the right side it can beactually seen as a combination that is composed of crank-rocker mechanism and the crank slider mechanism in whichthe crank-rocker mechanism consists of crank drive partswhere BC serves as a rocker and the crank slider mechanismconsists of a driving part (DB) and die-cutting machineplatform for slide block

2 Kinematic Analysis of theDie-Cutting Machine with theDual-Elbow-Bar Mechanism

Considering that the driving mechanism of dual-elbow-barcutting machine is 10th-rod and 3rd-level institutions it isaccurate and simple to use plural vector method to analyzeand calculate the law ofmotion rod First we need to establishthe displacement closed vector equation of the rods secondwe could convert them into nonlinear equations by Eulerrsquosformula in the end we can solve the equations to get the ruleof movement by MATLAB programming [11 12]

Based on Figure 1 we can set up the displacement closedvector equations of two-level institutions It is as follows

9978881198971+9978881198972=9978881198978+9978881198979+9978881198974

9978881198971

1015840

+9978881198972

1015840

=9978881198978

1015840

+9978881198979

1015840

+9978881198974

1015840

(1)

0 01 02 03 04 05 06minus40

minus30

minus20

minus10

0

10

20

30

40

Time t (s)

Ang

ular

acce

lera

tion

120572(r

ads

2)

Figure 2 The angular acceleration of BC and B1015840C1015840

Then carry out (1) in the plural form expression withEulerrsquos formula in which the real parts and imaginary partsare equal

1198971cos 1205791+ 1198972cos 1205792= 1198978cos 31205872+ 1198979+ 1198974cos 1205794

1198971sin 1205791+ 1198972sin 1205792= 1198978sin 31205872+ 1198974sin 1205794

1198971cos 12057910158401+ 1198972cos 12057910158402= 1198978cos 31205872+ 1198979+ 1198974cos 12057910158404

1198971sin 12057910158401+ 1198972sin 12057910158402= 1198978sin 31205872+ 1198974sin 12057910158404

(2)

Assuming that the maximum cutting pressure of die-cuttingmachine is 300 tons the highest cutting speed is 6000ticketshour the precision of die-cutting is 01mm the strokeof die-cutting platform is 25mm and the host power is 15 KWBased on the result of (2) we can establish the rod kinematicsequation and solve the motion equations of mechanism byMATLAB numerical analysis software programming At lastvariation curves of angular acceleration can be obtained inMATLAB drawing circumstance of double toggle compo-nents within a single cycle

As showed in Figure 2 when the maximum angularacceleration has reached nearly 30 rads2 the connecting rodis the weak parts of the mechanism which has a biggerimpact and greater effect on its fatigue strength As shownin Figure 3 when BD and B1015840D1015840 rod that connect with thecutting platform reach the top of the cutting it will have animpact on the cutting platform with the acceleration morethan 40 rads2 Since the cutting platformmechanism is largein size and weight this means the platform has great inertiaforce in the process of movement that poses a great impacton the drivingmechanism and affects the kinematic precisionseriously

Advances in Materials Science and Engineering 3

Table 1 The function requirements with alloy composition

Functional requirements Strength Plasticity Toughness Corrosionresistance Weldability

Alloy composition C Mn Nb CrS P

C Mn NbS P

C Nb Mn TiS P Cr

C P S CuCr Ni Al

C Mn S PCu Ni Cr

0 01 02 03 04 05 06minus50

minus40

minus30

minus20

minus10

0

10

20

30

40

50

Time t (s)

Ang

ular

acce

lera

tion

120572(r

ads

2)

Figure 3 The angular acceleration of BD and B1015840D1015840

3 Optimum Design forMechanism and Material Properties ofthe Driving Mechanism

The motion of dual-elbow-bar has a great influence on theperformance of the machine When reaching the peak accel-eration it will produce a larger impact load And then themotion of cutting platform does not conform to the processrequirements All about these conclusions will serve as theparameter of structural optimization design At present weneed to find a new drivingmechanism to replace the originalwhich can improve the motion characteristics so that onenot only can achieve the cutting process requirement but alsomakes the mechanism as simple as possible In the designof cam mechanism dual-elbow-bar part should be retainedas much as possible so that the contour surface can avoidbearing larger load(1) First of all the material of the camrsquos alloy composition

should be confirmed based on the working properties Thetraditional design is often preceded designed chemical com-position of alloy steel by experience and then process designHowever the lack of design in accordance with the axiommeets neither the design axiom between functional domainand the physical domain nor the design between the phys-ical domain and process domain [13] After QFD (QualityFunction Deployment) transforming the function demandsare strength plasticity toughness corrosion resistance andweldability

According to the experience the alloy composition andother influential components are listed in Table 1

C998400

B 998400

D998400

E 998400

O

D

B

C

Figure 4 Conjugate cam driving mechanism

The design method mentioned above can be representedby axiomatic design in Formula (3) as follows

strength FR1plasticity FR2

impact energy FR3corrosion resisitance FR4

weldability FR5

=

[[[[[

[

1 0 1 0 0 1 1 1 0 1

1 0 1 0 0 1 1 1 0 0

1 1 1 0 0 1 1 1 0 1

1 0 0 1 1 1 1 0 1 0

1 0 1 1 1 1 1 0 0 1

]]]]]

]

[[[[[[[[[[[[[[

[

C contentTi Mn Ni Cu S P Nb Al Cr

]]]]]]]]]]]]]]

]

(3)

According to the axiomatic design shown in Figure 4in view of the functional requirement level decomposi-tion following the axiom of axiomatic design the couplingof material parameters and mechanism function can bereduced thus we can confirm the material of the camrsquos alloycomposition as 40crMo(2) Second themotion parameters of the cutting platform

should be determined as follows

(a) Work Speed According to the design requirements themaximum speed of original should be increased from 6000


300

200

100

0

0 100 200 300

minus100

minus200

minus300minus100minus200minus300

Y(m

m)

X (mm)

Figure 5 The contour curve of main cam

ticketshour to 7500 ticketshour so a cycle experienced that119879 = 36007500 = 048 s

(b)Holding Pressure TimeBased on the process requirementstheworking pressure holding time should not be less than 012seconds In this design it is 016 seconds

(c)TheMaximumAcceleration of Cutting Platform Insure thatthe inertia force which is conducive to the movement andavoid the large impact The value 119886 = 5ms2

(d) Lift and Return TimeDistribution Formaking the smoothoperation of themechanism the lift time is equal to the returntime namely 016 seconds

(e) Working Stroke According to the requirement the designof working stroke is 20mm

By using optimum design method to reverse the camoutline and then programming an accurate map of camprofile in the MATLAB the cam contour line coordinateswith the parameters of the equation are derived by meansof coordinate transformation [14] After each structuralparameter of conjugate cam contour coordinates equationsbeing determined we can obtain the contour coordinates ofcam rotating value inMATLAB equation as shown in Figures5 and 6

The contour of the conjugate cam drawing in MATLABis composed of a series of discrete points by the spline curvefitting As the coordinate data of these points are savedin Workspace data file in MATLAB we can get the three-dimensional entity graph of the conjugate cam structure bycalling in the coordinate data file of major and vice camprofile in SolidWorks [15]

300

200

100

0

0 100 200 300

minus100

minus200

minus300

minus100minus200minus300

Y(m

m)

X (mm)

Figure 6 The contour curve of pair cam

00 01 02 03 04 05Time (s)

000510152025

minus05

minus10

minus15

minus20

minus25

Ang

ular

vel

ocity

120596(r

ads

)

Figure 7 The angular velocity of BC and B1015840C1015840

4 Kinematics Simulation ofOptimized Mechanism

Once the geometric model that has been modeled in Solid-Works is put into ADAMS we can start the analysis andsimulation of mechanism dynamics

The optimized mechanism is composed of upper andlower toggle cam cutting platform rails and engine baseThe operating speed is 7500 ticketshour Adding the speeddriver for 1308 rads to the primary component of the inputshaft (connected with the conjugate cam) simulation time is048 s and step is 0001 s

By ADAMS simulation analysis we get the speed andangular acceleration movement of BC and B1015840C1015840 as shown inFigures 7 and 8The red solid line represents BC and the bluedotted line represents B1015840C1015840


200

100

00

00 01 02 03 04 05Time (s)

300

minus100

minus200

minus300

Ang

ular

acce

lera

tion

120572(r

ads

2)


5 Conclusion

By comparing the characteristic curve of dual-elbow-bardriving mechanism in the 6000 ticketshour and the conju-gate cam drivingmechanism in the 7500 ticketshour we canget the following conclusions

(1) Based on the QFD and axiomatic design the materialof the camrsquos alloy composition is confirmed as 40crMowhich can get favorable kinematic performance

(2) The symmetrical bars of conjugate camdrivingmech-anism such as BC and B1015840C1015840 shown in Figures 7 and 8have symmetric variation law of motion Their speedand angular acceleration movement are smooth andcontinuous without mutation

(3) The angular acceleration of the two elbow-bars ofdual-elbow-bar driving mechanism is more than40 rads2 but angular acceleration of the two elbow-bars of the conjugate cam driving mechanism is lessthan 30 rads2 which can reduce the impact load onthe die-cutting machine

Conflict of Interests

The authors declare that there is no conflict of interestsregarding the publication of this paper

Acknowledgments

This paper is supported by National Natural Science Foun-dation of China (Program no 51305152) by National NaturalScience Foundation of China (Program no 51405179) and bythe Fundamental Research Funds for the Central Universities(Program no 52902-0900206075)

References

[1] C Xue Chao Y Qi and X Wang ldquoThe mechanism analysisand experiment research about die-cutting pressurerdquo Journal ofBeijing Institute of Graphic Communication vol 19 no 2 pp39ndash42 2011

[2] J Xie andH-J Zou ldquoDynamic analysis of the double-elbow-barmechanism of automatic vertical platen die-cutterrdquo MechaneDesign and Research vol 21 no 3 pp 75ndash78 2005

[3] G Li and G Cheng ldquoAnalysis and research of die cutting platenpress mechanism and its motion compatiblenessrdquo Packagingand Food Machinery vol 21 no 5 pp 5ndash7 2003

[4] X Zhang S Chai and G Cheng ldquoMotion analysis andoptimum design of the dual-elbow-bar mechanism of thedie cutting machinerdquo Journal of Beijing Institute of GraphicCommunication vol 14 no 2 pp 32ndash34 2006

[5] L Yong H Hongyan and C Ganghu ldquoAnalysis of dual-elbow-bar groupmotion based on conversionmethodrdquoPrintingEngineering vol 3 pp 34ndash37 2007

[6] G Cheng and X Wang ldquoReliability analysis for kinematicsaccuracy on elbow-bar mechanism of automatic die cuttingmachinerdquo Chinese Mechanical Engineering vol 18 no 15 pp1786ndash1789 2007

[7] W Yanbin Z Qinghai and Z Haiyan ldquoCharacteristic researchof elbow-bar framework of blocking die-cutterrdquoMachineDesignand Research vol 21 no 1 pp 76ndash78 2005

[8] Y Qun and W Zhimin ldquoComputer emulation of the dual-elbow-bar mechanism of the die-cutting machinerdquo PackagingEngineering vol 27 no 6 pp 191ndash193 2006

[9] X Zhao and Y Li ldquoMotion simulation of the dual-elbow-barmechanismof the die-cuttingmachine based onADAMSrdquoLightIndustry Machinery vol 26 no 3 pp 11ndash13 2008

[10] F Fan and H Ding ldquoThe research and the application for therotary die-cutting machine drive technologyrdquo in Proceedingsof the International Conference on Mechanic Automation andControl Engineering (MACE rsquo10) pp 5914ndash5917 Wuhan ChinaJune 2010

[11] W Q Cao Linkage Analysis and Synthesis Science PressBeijing China 2002

[12] Y Song and D Jia MATLAB Numerical Analysis and Applica-tion Mechanical Industry Press Beijing China 2009

[13] N P Suh ldquoDesigning-in of quality through axiomatic designrdquoIEEE Transactions on Reliability vol 44 no 2 pp 256ndash2641995

[14] L Guo and S Guo ldquoDesign and simulation of cam figurerdquoMechanical Research amp Application vol 18 no 3 pp 95ndash992005

[15] C Liping Mechanical System Dynamics Analysis and ADAMSApplication Tutorial Tsinghua University Press Beijing China2005

Submit your manuscripts athttpwwwhindawicom

ScientificaHindawi Publishing Corporationhttpwwwhindawicom Volume 2014

CorrosionInternational Journal of

Hindawi Publishing Corporationhttpwwwhindawicom Volume 2014

Polymer ScienceInternational Journal of



CeramicsJournal of


CompositesJournal of

NanoparticlesJournal of



International Journal of

Biomaterials


NanoscienceJournal of

TextilesHindawi Publishing Corporation httpwwwhindawicom Volume 2014

Journal of

NanotechnologyHindawi Publishing Corporationhttpwwwhindawicom Volume 2014

Journal of

CrystallographyJournal of


The Scientific World JournalHindawi Publishing Corporation httpwwwhindawicom Volume 2014


CoatingsJournal of

Advances in

Materials Science and EngineeringHindawi Publishing Corporationhttpwwwhindawicom Volume 2014

Smart Materials Research



MetallurgyJournal of


BioMed Research International

MaterialsJournal of


Nano

materials


Journal ofNanomaterials


A

Bo

C

D

F

A998400

E998400

B998400

D998400

C998400

l1

l8

l2

l5

l3

l4

l9

1205795

1205791

1205792

1205793

1205794

s

2l7

120579998400

3

120579998400

1

120579998400

2

120579998400

4

l998400

9

l998400

2

l998400

4

l998400

3

l998400

5

l998400

1

Figure 1 The dual-elbow-bar driving mechanism of die-cuttingmachine

traditional design method which causes low processing effi-ciency production quality and accuracy and poor stability(2)Material selection is dependent on experience lacking ofguidance on using the QFD tool (3)The virtual simulationtechnology of optimization design method in the design ofdie-cutting machine is still not mature

The main die-cutting mechanism of die-cutting machinediagram is a ten-bar mechanism which is complex andsymmetrical as showed in Figure 1 In Figure 1 AA1015840 is thedriving crank AB and A1015840B1015840 are the connecting rods BCand B1015840C1015840 are the lower toggle rods BD and B1015840D1015840 are theupper toggle rods and DD1015840 is the cutting platform Sincethe mechanism is symmetrical from the right side it can beactually seen as a combination that is composed of crank-rocker mechanism and the crank slider mechanism in whichthe crank-rocker mechanism consists of crank drive partswhere BC serves as a rocker and the crank slider mechanismconsists of a driving part (DB) and die-cutting machineplatform for slide block

2 Kinematic Analysis of theDie-Cutting Machine with theDual-Elbow-Bar Mechanism

Considering that the driving mechanism of dual-elbow-barcutting machine is 10th-rod and 3rd-level institutions it isaccurate and simple to use plural vector method to analyzeand calculate the law ofmotion rod First we need to establishthe displacement closed vector equation of the rods secondwe could convert them into nonlinear equations by Eulerrsquosformula in the end we can solve the equations to get the ruleof movement by MATLAB programming [11 12]

Based on Figure 1 we can set up the displacement closedvector equations of two-level institutions It is as follows

9978881198971+9978881198972=9978881198978+9978881198979+9978881198974

9978881198971

1015840

+9978881198972

1015840

=9978881198978

1015840

+9978881198979

1015840

+9978881198974

1015840

(1)

0 01 02 03 04 05 06minus40

minus30

minus20

minus10

0

10

20

30

40

Time t (s)

Ang

ular

acce

lera

tion

120572(r

ads

2)


Then carry out (1) in the plural form expression withEulerrsquos formula in which the real parts and imaginary partsare equal

1198971cos 1205791+ 1198972cos 1205792= 1198978cos 31205872+ 1198979+ 1198974cos 1205794

1198971sin 1205791+ 1198972sin 1205792= 1198978sin 31205872+ 1198974sin 1205794

1198971cos 12057910158401+ 1198972cos 12057910158402= 1198978cos 31205872+ 1198979+ 1198974cos 12057910158404

1198971sin 12057910158401+ 1198972sin 12057910158402= 1198978sin 31205872+ 1198974sin 12057910158404

(2)

Assuming that the maximum cutting pressure of die-cuttingmachine is 300 tons the highest cutting speed is 6000ticketshour the precision of die-cutting is 01mm the strokeof die-cutting platform is 25mm and the host power is 15 KWBased on the result of (2) we can establish the rod kinematicsequation and solve the motion equations of mechanism byMATLAB numerical analysis software programming At lastvariation curves of angular acceleration can be obtained inMATLAB drawing circumstance of double toggle compo-nents within a single cycle

As showed in Figure 2 when the maximum angularacceleration has reached nearly 30 rads2 the connecting rodis the weak parts of the mechanism which has a biggerimpact and greater effect on its fatigue strength As shownin Figure 3 when BD and B1015840D1015840 rod that connect with thecutting platform reach the top of the cutting it will have animpact on the cutting platform with the acceleration morethan 40 rads2 Since the cutting platformmechanism is largein size and weight this means the platform has great inertiaforce in the process of movement that poses a great impacton the drivingmechanism and affects the kinematic precisionseriously





C Mn NbS P

C Nb Mn TiS P Cr

C P S CuCr Ni Al

C Mn S PCu Ni Cr

0 01 02 03 04 05 06minus50

minus40

minus30

minus20

minus10

0

10

20

30

40

50

Time t (s)

Ang

ular

acce

lera

tion

120572(r

ads

2)






C998400

B 998400

D998400

E 998400

O

D

B

C





weldability FR5

=

[[[[[

[

1 0 1 0 0 1 1 1 0 1

1 0 1 0 0 1 1 1 0 0

1 1 1 0 0 1 1 1 0 1

1 0 0 1 1 1 1 0 1 0

1 0 1 1 1 1 1 0 0 1

]]]]]

]

[[[[[[[[[[[[[[

[


]]]]]]]]]]]]]]

]

(3)





300

200

100

0

0 100 200 300

minus100

minus200


Y(m

m)

X (mm)









300

200

100

0

0 100 200 300

minus100

minus200

minus300


Y(m

m)

X (mm)


00 01 02 03 04 05Time (s)

000510152025

minus05

minus10

minus15

minus20

minus25

Ang

ular

vel

ocity

120596(r

ads

)







200

100

00

00 01 02 03 04 05Time (s)

300

minus100

minus200

minus300

Ang

ular

acce

lera

tion

120572(r

ads

2)


5 Conclusion







Acknowledgments


References























CeramicsJournal of







Biomaterials




Journal of


Journal of





CoatingsJournal of

Advances in








MaterialsJournal of


Nano

materials







C Mn NbS P

C Nb Mn TiS P Cr

C P S CuCr Ni Al

C Mn S PCu Ni Cr

0 01 02 03 04 05 06minus50

minus40

minus30

minus20

minus10

0

10

20

30

40

50

Time t (s)

Ang

ular

acce

lera

tion

120572(r

ads

2)






C998400

B 998400

D998400

E 998400

O

D

B

C





weldability FR5

=

[[[[[

[

1 0 1 0 0 1 1 1 0 1

1 0 1 0 0 1 1 1 0 0

1 1 1 0 0 1 1 1 0 1

1 0 0 1 1 1 1 0 1 0

1 0 1 1 1 1 1 0 0 1

]]]]]

]

[[[[[[[[[[[[[[

[


]]]]]]]]]]]]]]

]

(3)





300

200

100

0

0 100 200 300

minus100

minus200


Y(m

m)

X (mm)









300

200

100

0

0 100 200 300

minus100

minus200

minus300


Y(m

m)

X (mm)


00 01 02 03 04 05Time (s)

000510152025

minus05

minus10

minus15

minus20

minus25

Ang

ular

vel

ocity

120596(r

ads

)







200

100

00

00 01 02 03 04 05Time (s)

300

minus100

minus200

minus300

Ang

ular

acce

lera

tion

120572(r

ads

2)


5 Conclusion







Acknowledgments


References























CeramicsJournal of







Biomaterials




Journal of


Journal of





CoatingsJournal of

Advances in








MaterialsJournal of


Nano

materials




300

200

100

0

0 100 200 300

minus100

minus200


Y(m

m)

X (mm)









300

200

100

0

0 100 200 300

minus100

minus200

minus300


Y(m

m)

X (mm)


00 01 02 03 04 05Time (s)

000510152025

minus05

minus10

minus15

minus20

minus25

Ang

ular

vel

ocity

120596(r

ads

)







200

100

00

00 01 02 03 04 05Time (s)

300

minus100

minus200

minus300

Ang

ular

acce

lera

tion

120572(r

ads

2)


5 Conclusion







Acknowledgments


References























CeramicsJournal of







Biomaterials




Journal of


Journal of





CoatingsJournal of

Advances in








MaterialsJournal of


Nano

materials




200

100

00

00 01 02 03 04 05Time (s)

300

minus100

minus200

minus300

Ang

ular

acce

lera

tion

120572(r

ads

2)


5 Conclusion







Acknowledgments


References























CeramicsJournal of







Biomaterials




Journal of


Journal of





CoatingsJournal of

Advances in








MaterialsJournal of


Nano

materials










CeramicsJournal of







Biomaterials




Journal of


Journal of





CoatingsJournal of

Advances in








MaterialsJournal of


Nano

materials



Research Article Optimum Design for Mechanical Structures...

Documents

Transcript of Research Article Optimum Design for Mechanical Structures...