1st Euro-Mediterranean Conference on Structural Dynamics and Vibroacoustics, Medyna2013 -...

8/16/2019 1st Euro-Mediterranean Conference on Structural Dynamics and Vibroacoustics, Medyna2013 - Proceedings

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1st Euro-Mediterranean Conference on Structural

Dynamics and Vibroacoustics

PROCEEDINGS

!-" #$ril %1! Marra&ec' (Morocco)


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!r"ani#in" associations!r"ani#in" associations!r"ani#in" associations!r"ani#in" associations

ADY$A% A &rench association 'or tructural Dnamics and $ibroacoustics created in *0++

&A-G$B% The $ibroacoustic "rou, o' the &rench ociet o' Acoustics

A$A% The oroccan Association 'or Acoustic and $ibration

ATA$% The Tunisian association 'or Acoustic and $ibration

!A% The nstitute o' Acoustic o' the Chinese Academ o' ciences

!r"ani#in" Board!r"ani#in" Board!r"ani#in" Board!r"ani#in" Board

anuel Collet (&/T!-T CN12 &rance) - General Chair

ohamed chchou (TD /C2 &rance) - General Co-Chair

Charles 4#erat (A5 5niv du aine2 &rance) - Technical ro"ram Co-Chair

1hali Benamar (/ - 5m6a2 orocco) - 1e"ional ro"ram Co-Chair orocco

ohamed 7addar (/N2 Tunisia) - 1e"ional ro"ram Co-Chair Tunisia

&ushen" ui (!A-CA2 China) - 1e"ional ro"ram Co-Chair Asia

/mmanuel &olt8te (&/T!-T /N2 &rance) - !r"ani#in" Committee Co-Chair Treasurer

7onorar Chairs7onorar Chairs7onorar Chairs7onorar Chairs

Daniel 9uv4 (ro'essor /cole Centrale de on)

Anders Nilsson (1oal nstitute o' Technolo"2 toc:holm)

1o"er !haon (/meritus ro'essor CNA2 aris)

9in" Tian (resident o' Acoustical ociet o' China)

cienti'ic Committeecienti'ic Committeecienti'ic Committeecienti'ic Committee

a:rem Ar'aoui (/NT2 TN)

ierre Ar"oul (/NC2 &1)

9. 1oberto Arruda (5nicam,2 B1)

Noureddine Atalla (GA52 CAN)

ohamed Belha; (&AC2 A)

abrou: Ben Tahar (5TC2 &1)

Noureddine Bouhaddi (&/T!2 &1)

Claude Boutin (/NT/2 &1)

cott Co"an (&/T!-T2 &1)

ois Gautier (A52 &1)

Bilal 7arras (&T &es2 A)

9ean-Claude Golinval (5G2 B/)

ohamed-Ali 7amdi (5TC2 &1)

ot'i 7ammami (/N2 TN)

9an 7olnic:i (T2 !)

/ric 9ac;uelin (5CB2 &1)

Cha'i:


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Con'erenceCon'erenceCon'erenceCon'erence in'ormationin'ormationin'ormationin'ormation

1e"istration1e"istration1e"istration1e"istration

The re"istration des: ill be o,en 'rom .00 to +E.30 on Tuesda *3rd2 'rom .30 to +E.00 on =ednesda *Fth 9ul and 'rom .+6 to +3.00 on Thursda *6

th A,ril. /ach re"istered ,erson ill

receive a con'erence bad"e2 con'erence ,ro"ram and ba" at the con'erence re"istration and chec:-in

area. lease ear our bad"e at all times. n our ba" ou ill 'ind a 5B drive ith the

,roceedin"s o' the con'erence. There ill be no ,rinted boo: o' abstracts.

$enues $enues $enues $enues

The o,enin" and closin" ceremonies and ,lenar lectures ill ta:e ,lace in the Yves 1ocard

am,hitheater. ,ecial sessions and contributed tal:s ill ta:e ,lace in ,arallel sessions in the Yves

1ocard am,hitheater and in the lecture rooms (Daa-You aa2 Al-


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nvited s,ea:ersnvited s,ea:ersnvited s,ea:ersnvited s,ea:ers

Adnan Akay (Bilkent University, Ankara, Turkey & Carnegie

Mellon University, USA)

Dr. A:a started his tenure at Carne"ie ellon as a ,ro'essor and head o' theechanical /n"ineerin" De,artment in +JJ*. n +JJE2 he as aarded the endoed

ord Chair in /n"ineerin". Beteen *006 and *002 Dr. A:a served as the Director o'

Civil2 echanical and anu'acturin" nnovation Division at the National cience

&oundation. Currentl he is on leave o' absence at Bil:ent 5niversit in An:ara2 Tur:e

servin" as $ice resident and ro'essor2 and 'oundin" head o' the echanical /n"ineerin" De,artment. ro'essor

A:a has held visitin" a,,ointments at the T Aeronautics and Astronautics De,artment2 the 5niversit o'

1ome Ka a,ien#a2K and NA on in &rance and other institutions. Dr. A:a continues to serve as a member

o' industr boards and re"ularl consults ith international industries as a technical advisor and serves on

advisor boards o' several universities and "overnment a"encies includin" the 5 N& - Taian NC ummernstitute on Bio-ins,ired ensin" L Bio-ins,ired Actuation Technolo". ro'essor A:a is an active member o' the

en"ineerin" ,ro'essional communit2 and has been reco"ni#ed 'or his contributions to research2 education and

,ro'essional service. ro'essor A:a is the reci,ient o' the A/ er Br?el Gold edal (*006) and 7umboldt

1esearch Aard (*0++). 7e is a 'ello o' the American ociet o' echanical /n"ineers2 a 'ello o' the Acoustical

ociet o' America2 and a member o' several honor societies. ro'essor A:as research lies in a,,lied mechanics

ith em,hasis on vibrations2 acoustics2 tribolo"2 and dissi,ation theories. 7is earlier research that addressed

im,act and transient noise mathematicall described conversion o' ener" associated ith the acoustic mass to

sound durin" transient motion. 7is or: on 'luid-laer dam,in" later led to a discover and visuali#ation o'

streamin" that develo,s ithin a thin 'luid laer. uch o' his current research 'ocuses on 'riction-induced sounds

and on contact dam,in". A current collaborative research ,roHect ith the 5niversit o' 1ome a,,lies the conce,t

o' thermali#ation o' vibrations2 ins,ired b the dnamics o' atoms in a solid2 to reduce vibrations in com,le@

structures. This or: is no e@tended to model dissi,ation in thermal baths that surround nano-scale devices. 7is

current research ith collea"ues at NA-on 'ocuses on measurement and modelin" o' ,arameters that can

describe tactile sensation and ave "eneration beteen slidin" sur'aces.

ound and $ibration &rom &riction Beteen o't aterials 5nder i"ht oadsound and $ibration &rom &riction Beteen o't aterials 5nder i"ht oadsound and $ibration &rom &riction Beteen o't aterials 5nder i"ht oadsound and $ibration &rom &riction Beteen o't aterials 5nder i"ht oads

5nderstandin" the ,ro,erties and conse;uences o' 'riction under li"ht normal loads is 'undamental to 'urther

advancin" areas such as tactile sensin"2 ha,tic sstems used in robotic "ri,,in" o' sensitive obHects2 and

characteri#ation o' ,roducts that ran"e 'rom the so'tness o' 'abrics to e''ects o' sur'actants2 such as lotions2 ons:in. n tactile sensin"2 as a 'in"er is li"htl rubbed over a sur'ace2 the mechanorece,tors in the dermis become

e@cited and send si"nals to the brain 'or ,rocessin". Their e@citation results 'rom the as,erities2 adhesion2 and

other "eometric and chemical sur'ace ,ro,erties that come into contact ith the s:in. These same sources also

"ive rise to vibration and sound as to sur'aces are in slidin" contact even under li"ht load2 such as a 'in"er ,ad

over a sil: 'abric. =hereas the mechanorece,tors res,ond around *00 - 300 7ert#2 s,ectrum o' the actual sounds

and vibrations that are "enerated can "o beond these values2 thus ,resentin" additional o,,ortunities 'or sur'ace

characteri#ation throu"h acoustic res,onse. A modest bod o' literature e@ists on the acoustic res,onse o' so't

sur'aces under 'riction. 7oever2 onl a limited number o' those address 'riction sounds and vibrations under

li"ht loads. uch o' the ,revious or: in this area relates to ,erce,tion and tactile sensin" ith limited attention

to the "eneration mechanisms o' sound and vibration beteen so't sur'aces. This ,a,er describes a ne a,,aratus

to measure 'riction simultaneousl ith dnamic ;uantities such as accelerations2 'orces2 and sound ,ressures

resultin" 'rom a li"ht contact over a so't material2 much li:e a 'riction 'in"er li"htl rubbin" over a so't material.


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Jérôme Buffe (Tales Alenia S!ace, FR)

7ead o' the mechanical de,artment o' T7A/ Alenia ,ace2 atellites and

telecommunication Branch (CANN/). General Coordinator o' mechanical

activities across T7A/ Alenia ,ace. enior ember o' the 3A& (Aeronautics

Astronautics &rench Association) into the KtucturesK Commission. Activemember in the develo,ment and im,lementation o' /uro,ean standardi#ations in the s,ace sector

(/C) and es,eciall 'or the mechanical as,ects.

Ne considerations on the validation and on the o,timi#ation o' desi"nsNe considerations on the validation and on the o,timi#ation o' desi"nsNe considerations on the validation and on the o,timi#ation o' desi"nsNe considerations on the validation and on the o,timi#ation o' desi"ns in the s,ace domainin the s,ace domainin the s,ace domainin the s,ace domain

' there is one domain here o,timi#ations on the desi"ns are mandator ith re"ard to the mass

constraints2 here the reliabilit on the ,er'ormances has to be ell handled and here dnamic

and static environments are o' 'irst im,ortance2 there are2 'or sure2 the s,ace activities and more

s,eciall the satellites.

The aim o' this ,ro,osed ,resentation 'or edna *0+3 con'erence is to tal: about the di''erent

as o' dealin" ith the ;uestion o' this com,le@ situation and the com,romise hich has to be

'ound. The current a is commonl called a deterministic ,rocess b usin" standard rules

hatever the desi"ns and b minimi#in" the sa'et mar"ins. Another a is to use a ,robabilistic

a,,roach alloin" the decider to desi"n at an o,timi#ed technico economic level ith re"ard to the

,er'ormances and their criticalit. &inall2 another a could be to use a robustness a,,roach hen

a lac: o' :noled"e on the characteristics is there.

This ne consideration on the validation o' the desi"ns is more and more u, to date since the

variabilit on the characteristics o' the com,onents and on the elementar ,ieces is increasin". The

industrial orld2 even in s,ace 'ield2 is 'aced to some evolutions dealin" ith eventual di''erent

characteristics to those alread seen in the ,ast and2 so2 im,actin" the current rules 'or validation

and2 b conse;uence2 the o,timi#ations.

!therise2 due to the so ver 'e numbers o' s,ecimens involved in the satellites ,roduction and

ith a so scattered "roin" distribution o' the ,er'ormances2 the ,hiloso,h 'or an ade;uate

;uali'ication b test is also im,acted ith an a,,ro,riate choice on models andOor ith a validation

b an analtical ,rocess to be done in ,arallel. As a conclusion2 the ,resentation ill be 'ocused on the sensiti#ation o' this ne situation hich

could be relativel critical 'or satellites and on the interest o' some ne methods to ,ut into ,lace in

order to handle as much as ,ossible the desi"ns and to "et the most a,,ro,riate solution 'or the

o,timi#ation and robustness ,ur,oses.

n that conte@t2 a ,ertinent vie has to be ,rovided on the desi"ns and their robustness. The ris:

analsis on the 'inal obHective to be reached 'or the satellite ,er'ormance has to be done b usin"

the "roin" com,le@it o' the situations to be met. ore than ,reviousl2 the decision 'or the

research o' the best desi"n throu"h a ,robabilistic a,,roach or a robustness a,,roach in its choicehas to be ta:en 'or the most e''icient 'inal ,roduct ith the technico economic "oals.


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Peter Eberhard (University o" Stuttgart, #E)

eter /berhard is &ull ro'essor o' echanics and Director o' the nstitute o'

/n"ineerin" and Com,utational echanics at the 5niversit o' tutt"art in

German. 7e studied echanical /n"ineerin" ith 'ocus on Dnamics and

Control and did his doctoral de"ree on o,timi#ation o' mechanical sstems andhis habilitation about contact ,roblems. A'ter a ,ro'essorshi, at the 5niversit

/rlan"en-Nurember" he Hoined the 5niversit o' tutt"art. 7e and his coor:ers research interests

include ultibod stems2 Contact echanics (es,eciall ,articles)2 !,timi#ation2 echatronics

and Control2 Biomechanics2 and 5ncertainties. 7e received the 1ichard-von-ises-Aard and he

holds a 7onorar ro'essorshi, 'rom the NanHin" 5niversit o' cience and Technolo" in China.

7e is author and coauthor o' several boo:s and about *E6 scienti'ic ,a,ers.

odern odel 1eduction in Dnamicsodern odel 1eduction in Dnamicsodern odel 1eduction in Dnamicsodern odel 1eduction in Dnamics ---- much more than Hust a athematical To much more than Hust a athematical To much more than Hust a athematical To much more than Hust a athematical To

n this tal: some introduction to the model reduction o' elastic structures is "iven so that these

hu"e models can be used in a dnamic multibod simulation. Durin" the last decade there as a lot

o' research activit "oin" on and the 'ocus shi'ted 'rom modal methods to a,,roaches usin"

moment-matchin" or balanced truncation. These methods are not Hust mathematicall beauti'ul but

are also ver use'ul 'or en"ineerin" a,,lications. /@am,les ill be shon includin" also

com,arisons ith di''erent methods. A s,ecial 'ocus ill be on the model reduction o' cou,led

elastic structures.


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Daniel Juvé (Ecole Centrale $e %yon, FR)

ro'essor at /cole Centrale de on2 head o' the Centre Acousti;ue and head o'

the e@cellenc laborator on Acoustics (CeA) . 1esearch interests concern%

"eneration o' sound b turbulent 'losI subsonic and su,ersonic HetsI "ra#in"

'los over cavitiesI all-,ressure 'luctuations and ro,a"ation o' acoustic avesin non-homo"eneous and random movin" mediaI micrometeorolo"ical e''ects in

atmos,heric sound ,ro,a"ation. ro' D. 9uv4 as aarded Chavasse ri#e o' the &rench Acoustical

ociet (+JJ0) Great ri#e Ale@andre 9oannidPs o' the &rench Academ o' ciences (*00+2 to"ether

ith Christo,he Baill)2 'ello o' the Acoustical ociet o' America (+JJ)2 associate 'ello in the

American nstitute o' Aeronautics and Astronautics (AAA2 *00J)2 member o' the &rench Acoustical

ociet (&A)2 o' the &rench Association 'or Aeronautics and ,ace (AAA&)2 o' the &rench ociet

o' echanics (A&). 7e is editor o' the 9ournal o' ound and $ibration (Acoustics) and the

nternational 9ournal o' Aeroacoustics. 7e is member o' the Aeroacoustics ,ecialists Committee o'

the Council o' /uro,ean Aeros,ace ocieties (C/A- AC)2 /valuation and !rientation Committee

o' De,artment DNA o' !nera2 ana"ement Committee o' the &rench Netor: on Aeroacoustics

1!Q5A and cienti'ic Committee o' the &rench 1esearch &oundation 'or Aeronautics and ,ace

(&1A/).

Turbulent allTurbulent allTurbulent allTurbulent all----,ressure 'luctuations% models and relati,ressure 'luctuations% models and relati,ressure 'luctuations% models and relati,ressure 'luctuations% models and relation ith 'luid dnamics com,utationson ith 'luid dnamics com,utationson ith 'luid dnamics com,utationson ith 'luid dnamics com,utations

odelin" all-,ressure 'luctuations beneath a turbulent boundar laer is an im,ortant issue 'or

the ,rediction o' 'lo-induced structural vibrations and subse;uent noise emission.

n this tal: e ill 'irst "ive a short revie o' current models o' ,oint-s,ectra2 s,atial correlations

and cross-s,ectra o' turbulent ,ressure 'luctuations. The ,ossibilit o' usin" 'luid dnamics

com,utations (avera"ed R1ANS com,utations or time-resolved R/S) to identi' the various 'lo

,arameters used in these models ill be discussed. &inall recent results obtained in measurin" or

com,utin" the RacousticS com,onent (associated ith su,ersonic avenumbers) o' all-,ressure

'luctuations ill be ,resented to"ether ith a ne e@,erimental set-u, desi"ned to stud the e''ect

o' 'avorable or adverse mean-,ressure "radients.


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Anders Nilsson (Royal nstitute o" Tecnology, Stockol', SE)

Anders Nilsson holds c in /n"ineerin" hsics 'rom 5niversit o' und2

eden and Dr.Tech. in ound and $ibration 'rom Chalmers 5niversit.

Anders Nilsson has or:ed on ,roblems relatin" to the ,ro,a"ation o' sonic

booms at Boein" Co.2 eattle 2 5A. At Det Nors:e $eritas he became head o'the Acoustics De,artment at the 1esearch Division. At $eritas Anders Nilsson or:ed on the

,ro,a"ation o' structure borne sound in lar"e built u, structures li:e shi,s and on the e@citation o'

,lates 'rom 'lo and cavitation. Anders Nilsson as head o' the Danish Acoustical nstitute 'or 'our

ears. 7is main activit in Denmar: as buildin" acoustics. n +JE Anders Nilsson as a,,ointed

,ro'essor o' A,,lied Acoustics at


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Goran Pavic (SA %yon, FR)

Goran avi holds Bc in echanical /n"ineerin" and hD in Acoustics and

$ibration. A'ter havin" s,ent *F ears in research in shi,buildin"2

electrotechnical and mechanical industries2 he as elected to ,ro'essorshi, at

the National nstitute o' A,,lied ciences in on2 &rance. 7is duties involveresearch and teachin" in vibration2 acoustics and si"nal ,rocessin".

The ,resent research activities o' G. avi are in the areas o' vibroacoustics o' mechanical sstems2

virtual noise snthesis and ener" related techni;ues o' sound and vibration analsis. G. avi has

,artici,ated in J international ,roHects concernin" noise and vibration2 out o' hich in F as the

coordinator2 in several tens o' industr 'unded ,roHects as ell as in the /uro,ean Doctorate in

ound and $ibration ,ro"ramme. 7e is 'ormer associate editor o' Acta Acustica and current

associate editor o' Technical AcousticsI 'ormer director o' nternational nstitute o' Acoustics and

$ibration and member o' * ! standardisation committees. 7e has ,ublished a number o' Hournal

articles and has ,resented a number o' ,a,ers on various to,ics in the 'ield o' sound and vibration.

$irtual Noise nthesis $irtual Noise nthesis $irtual Noise nthesis $irtual Noise nthesis

The snthesis o' noise o' an industrial ,roduct can be done b sub-structurin" it into its basic

com,onents. A ,articular sub-structurin" method ,redicts the trends in the overall noise b

combinin" data 'rom the real source(s) ith a sim,li'ied modellin" o' the main 'rame. The cou,lin"

beteen the source(s) and the 'rame is ensured b im,edance cou,lin" rules. The criticalcom,onents are the noise sources hich have to be characterised b measurements. The

characterisation techni;ues are not sim,le2 but reveal a lot o' use'ul in'ormation to the desi"ner

a,art 'rom ,rovidin" the in,ut data to snthesis method itsel'. The sim,li'ied 'rame model has the

advanta"e o' bein" robust and eas to im,lement. The out,ut o' the snthesis is the noise level and

the noise ave'orm 'or audible re,roduction. The ,a,er outlines the basics o' the source

characterisation techni;ues and o' the noise snthesis a,,roach accom,anied b several e@am,les.


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Pedro ibeiro (Faculty o" Engineering, University o" Porto, PT)

edro 1ibeiro earned a Doctor o' hiloso,h de"ree at the nstitute o' ound

and $ibration 1esearch ($1)2 5niversit o' outham,ton2 in +JJ. 7e

currentl is an Assistant ro'essor at the De,artment o' echanical

/n"ineerin"2 &acult o' /n"ineerin" o' the 5niversit o' orto2 here helectures subHects in the area o' A,,lied echanics.

7is research 'ield is nonlinear dnamics o' structures2 mainl ith "eometrical nonlinearit2 but

ith some incursions into ,lasticit. 7e has been and is involved in research ,roHects related ith

nonlinear dnamics o' structures. Currentl he su,ervises to hD theses in non-linear oscillations

o' com,osite laminates.

edro 1ibeiro is author or co-author o' over 'ort international Hournal ,a,ers. 7e ,resent several

communications in con'erences and other international meetin"s2 ,resented seminars in diverse

universities and lectured in C advanced school R/@,loitin" Nonlinear Behaviour in tructural

DnamicsS in *0+0. 7e as chairman o' /51!/C7 Collo;uium F32 RGeometricall non-linear

vibrations o' structuresS in *00E2 has been involved in the or"ani#ation o' a 'e sm,osia and acted

as co-editor o' Hournal s,ecial issues related ith nonlinear dnamics.

NonNonNonNon----linear modes o' vibration o' structural elementslinear modes o' vibration o' structural elementslinear modes o' vibration o' structural elementslinear modes o' vibration o' structural elements

=hen structures e@,erience lar"e am,litude vibrations2 some characteristics ,resent in modes o'

vibration o' linear sstems are not ,reserved. t is intended in this ,resentation to e@,lore the

e@tension o' the mode o' vibration notion to vibrations in the "eometricall non-linear re"ime.

A'ter a short revie on or: and conce,ts ,resented b di''erent authors2 the ,resentation ,roceeds

to the analsis o' ,eriodic2 conservative2 'ree vibrations o' structural elements2 s,eci'icall beams2

,lates and shells. &or that ,ur,ose2 the dis,lacement com,onents are e@,anded as sums o' ,roducts

o' 'unctions o' time and 'unctions o' s,ace. =ritin" the time 'unctions as truncated &ourier series2

sets o' al"ebraic e;uations in the 're;uenc domain are derived and2 b solvin" these e;uations2 one

can investi"ate the variation o' 're;uenc and sha,e o' vibration ith the vibration am,litude. =ith

the ,rocedures ,resented2 it is also ,ossible to analse internal resonances2 that is2 cou,lin"s

beteen modes that are induced b the non-linearit and that lead to interestin" oscillations.


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!assimo u""ene (eorgia nstitue o" Tecnology, Atlanta, US)

assimo 1u##ene is a ro'essor in the chools o' Aeros,ace and echanical

/n"ineerin" at Geor"ia nstitute o' Technolo". 7e received a h.D in

echanical /n"ineerin" 'rom the olitecnico di Torino (tal) in +JJJ. 7e is

author o' a,,ro@imatel +06 Hournal ,a,ers and about +30 con'erence ,a,ers2and has ,artici,ated as a or co- in various research ,roHects 'unded b

the Air &orce !''ice o' cienti'ic 1esearch (A&!1)2 the Arm 1esearch !''ice (A1!)2 the !''ice

o' Naval 1esearch (!N1)2 NAA2 the 5 Arm2 T1= Cor,oration2 DA1A and the National

cience &oundation (N&). ost o' his current and ,ast research or: has dealt ith structural

health monitorin"2 ave ,ro,a"ation analsis2 hi"h 're;uenc vibration modelin"2 and vibration

and noise control techni;ues. . 1u##ene is a &ello o' A/2 and member o' AAA2 A72 and

AA.

Nonlinearities and multi'ield interactions 'or ada,tive metamaterialsNonlinearities and multi'ield interactions 'or ada,tive metamaterialsNonlinearities and multi'ield interactions 'or ada,tive metamaterialsNonlinearities and multi'ield interactions 'or ada,tive metamaterials

etamaterials consist o' en"ineered microstructural assemblies that e@hibit su,erior ,ro,erties in

com,arison to less-com,osed or naturall-occurrin" materials. Their unusual ave ,ro,erties

include band-"a, behavior2 res,onse directionalit2 le't-handedness2 and ne"ative acoustic re'raction2

amon" others. These 'eatures2 and their a,,lication 'or the desi"n o' acoustic 'ilters2 ave"uides2

lo"ic ,orts2 and ultrasonic transducer arras2 motivate the investi"ation o' elastic ave ,ro,a"ation

in micro-structured media.

The seminar ,resents in ,articular the directional ,ro,erties o' ,eriodic media2 as de'ined b their

abilit to direct aves in ,re'erential direction. uch ,ro,erties are 'irst illustrated on sim,le s,rin"-

mass sstems2 and subse;uentl demonstrated in com,le@ structural lattices o,eratin" in linear and

nonlinear de'ormation re"imes. n addition2 ,eriodic arras o' electromechanical resonators2 and

lattices that under"o to,olo"ical chan"es resultin" 'rom structural instabilities are discussed as

e@am,les o' ada,tive metamaterials. Tunable local resonatin" sstems2 and local instabilities are

investi"ated as e''ective means to ,rovide the considered ,eriodic assemblies ith ada,tive

band"a,s and ave steerin" characteristics.


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Jin# $ian (Presi$ent o" Acoustical Society o" Cina, C)

ro'essor TAN 9in"2 ,resident o' Chinese ociet o' AcousticsI 7onorar 'ello o'

nternational nstitute o' Acoustics and $ibration (A$)I /@ecutive /ditor in Chie' 'or

Acta Acustica2 Director member o' Technical Committee o' National Acoustical

tandardi#ation.

Graduated 'rom the De,artment o' hsics o' NanHin" 5niversit maHored in acoustics on

&ebruar +J*2 then he "ot his asters de"ree in +JF and his h.D. 'rom nstitute o' Acoustics2 Chinese

Academ o' ciences (ACA) on December +JJ+. As a researcher on electro-acoustic and noise control 'or more

than 30 ears2 ro'. Tian has been the ,rinci,al investi"ator 'or F0 research ,roHects su,,orted b various 'undin"

bodies includin" National inistr o' LT2 National Natural cience &oundation2 Chinese Academ o' ciences

(CA)2 and other or"ani#ations. The research covers several areas o' acoustics% active noise and vibration control2

electronic anti-noise communication devices2 audio characteristic si"nal control2 acoustical /2 transmission

and evaluation o' tra''ic noise and a,,lications o' 'inite am,litude sound ave.


15/455

Bernard $roclet (Senior E*!ert in Structural Mecanics, !ro"essor at

ES Cacan, FR)

Bernard T1!C/T is 1LD ,roHect mana"er (tructural /n"ineerin") in /AD

AT15 T and ,ro'essor at /N CAC7AN. 7e is en"ineer 'rom A/-

/NA (/cole Nationale u,4rieure de 4cani;ue et dA4ronauti;ue de

oitiers) and obtained is 7abilitation o' 1esearch in echanics L /ner"etics 'rom aris $. 7is

domains o' e@,ertise are Dnamics com,utation2 Acoustic2 deterministic and random $ibration2

id L 7i"h &re;uenc Analsis and rotechnic shoc:s.

nthesis o' Ariane F L Ariane 6 vibroacoustic studies and ,ers,ectivesnthesis o' Ariane F L Ariane 6 vibroacoustic studies and ,ers,ectivesnthesis o' Ariane F L Ariane 6 vibroacoustic studies and ,ers,ectivesnthesis o' Ariane F L Ariane 6 vibroacoustic studies and ,ers,ectives

The obHective o' this con'erence is to ,resent the vibroacoustic a,,roach on Ariane launchers. /arlin the desi"n develo,ment o' the Ariane 6 launcher2 it as antici,ated that the acoustic

environment ould be a severe case load. Conse;uentl2 ver soon2 noise reduction means have

been investi"ated.

This con'erence ill address%

• The acoustic environment e@,erienced b the launchers li't-o'' and durin" 'li"ht ascent and

the or: underta:en to reduce noise surroundin" the A1AN/ 6 launch vehicle and the

noise inside the &airin" on the one hand. The reduced scale test to characteri#e the li't-o''noise and to investi"ate ,otential noise reduction means2 the &airin" 'ull scale acoustic test

are ,resented2

• And the methods used to estimate the vibroacoustic res,onse o' launch vehicles on the

other hand.

&inall2 ,ers,ectives2 ,articularl in the 'ield o' mid 're;uenc res,onse ill be ,resented.


16/455

Eberhard Hau# (ES, #E)

/berhard 7au" is one o' the 'oundin" members o' / Grou,2 the ell-:non

virtual ,rotot,in" com,an2 here he held the ,osition o' cienti'ic Director.

7e is no retired and acts as a consultant. /berhard 7au" "raduated 'rom the

5niversit tutt"art (=.G.) in Civil /n"ineerin" and he earned his h.D. de"reein tructural /n"ineerin" at the 5niversit o' Cali'ornia2 Ber:ele2 here he

rote a ,ro"ram 'or the lar"e dis,lacement 'inite element analsis o' li"htei"ht cable and

membrane structures. 7e as a 1esearch Associate at the 5niversit o' tutt"art ith ro'essors

&rei !tto and 9.7. Ar"ris. At / Grou,2 he as the drivin" 'orce behind the develo,ment o'

various non-linear &/ analses ,ro"rams and material model develo,ments and he is the ,rinci,al

ince,tor o' the orldUs ,remier crash2 occu,ant sa'et and stam,in" simulation codes. 7is recent

com,utational develo,ments 'ocused on biomechanics. 7e has ,ublished man ,a,ers on the

theor and industrial a,,lication o' modern numerical simulation techni;ues. 7is recent consultin"

activities include the ind simulation o' li"htei"ht structures.

Numerical Desi"n and Analsis o' &le@ible tructuresNumerical Desi"n and Analsis o' &le@ible tructuresNumerical Desi"n and Analsis o' &le@ible tructuresNumerical Desi"n and Analsis o' &le@ible tructures

This article e@tends the a,,lication o' / Grou, roducts into the s,ectacular 'ield o' ,ecial and

i"htei"ht structures2 a domain situated in the 'ield o' hi"h-rise buildin" construction2 in recent

1asch Gmb7 and / &rance Hoint ,roHects.

/ Grou, is a "lobal com,a"n or:in" on $irtual ,rotot,in" and Testin" and is a ,ioneer in1ealistic &/ imulation2 in ,articular 'or ,re-certi'ication o' structural inte"rit ith res,ect o'

accidental and e@treme o,eratin" conditions. -1asch Gmb72 an internationall o,eratin"

architectural and en"ineerin" o''ice2 located in tutt"art2 German2 is s,eciali#ed in the architectural

and structural desi"n o' ,ecial and i"htei"ht structures2 o'ten made o' ,re-stressed 'le@ible

cables and membrane 'abrics. The industrial a,,lication o' this ,rinci,le as ,ioneered in the +J60-

s b the German architect ro'essor &rei !tto. &le@ible buildin"s made ith 'iber rein'orced

technical membranes are ,articularl sensitive to ind loads. / &rance has develo,ed2 calibrated

and validated an analsis and desi"n methodolo" to investi"ate ind load e''ects2 ran"in" 'romconstant ind velocit ,ro'iles to in,ut o' ind 'ields ith natural turbulence ("usts) (h.D. thesis

A. ichals:i). =hile 'or most conventional hi"h-rise buildin"s the structural res,onse to ind load

can be evaluated via com,utational 'luid.


17/455


18/455


19/455

Sessions

1:30 - 22:00 elcome eent

# l - 4 h

a " a r i ' m i

1=:.0 - 1;:10

>on linear modal anal+sis of d+namic absorbers

.athi D)emal, /5 Dion, .aher Chaari, 'mad

a9fiq, "ohamed +addar

etectin, and Measurin, Slu, $elocit+ in ?"o-

&hase (lo"s ori'ontal &i!es

"uammer *lssayh, *bdulma)id *ddali, Da#id"ba, *bdelhamid Naid

etermination of forces in risers used in the

!etroleum industr+ b+ indirect measurements

*le>andre %a9ano, *bdel-male &ine

1=:30 - 1=:.0

>onlinear "ae !ro!a,ation in !ost-bucled

structures

*lessandro S7adoni, .lorian 0aul "aurin

7 e s R o c a r d

?urbulent "all !ressure measurement in lo"

"aenumber usin, the flo"-induced ibrations

Damien Le(oq, Charles 0e1erat, /ean-hugh

homas, 2en7ing Bi

/ a a - 7 o u M a a

Model selection for the euation of motion

"i(hal Ru1e, /ean-Louis uyader, Charles

0e1erat

1;:10 - 1;:30

ela+ed feedbac controller in M5MS

resonators

%5 "asri, "5 Younis, S5 Shao

5)!erimental 9nesti,ation of the 5uilibrium

and Stabilit+ of @on, ?o"ed %able S+stems

"artin $bligado, "i(ael Bourgoin

9s hi,h-s!eed di,ital holo,ra!h+ the ultimate

tool for ibration anal+sis A

/ulien 0oitte#in, 0as(al 0i(art, .ran3ois autier,

Charles 0e1erat

1.:.0 - 1=:30

Nonlinear System dynamics

/o8l 0erret-Liaudet :!CL,.R;.lo# /nduced Vibrations and Noise

Lin Li :S/0, CN;

Vibration .ield Measurements and .orce

/dentification

Charles 0é1erat :L*?", .R;

offee brea!

0osters session

MD'N" ()*+% *st uro-Mediterranean onference on Structural Dynamics and Vibroacoustics

$uesday, "pril (+, ()*+

14:30 - 1.:10 &lenar+ 999 - Jing Tian :0resident of *(ousti(al So(iety of China, CN;

Chair< "ohamed '(h(hou

1.:10 - 1.:.0&lenar+ 9$ - Modern Model Reduction in Dynamics% much more than 1ust a Mathematical $oy b+ Peter Eberhard :?ni#ersi

Chair< "ohamed Belhaq


20/455


21/455

Sessions

18:.0 - 1:30 &lenar+ 9E - Numerical Design and "nalysis of .le4ible Structures b+ Eberhard Haug :!S', D!;Chair< .usheng Sui

1:30 - 23:00 5ala

1;:30 - 1;:.0

1=:.0 - 1;:10

>umerical simulation and e)!erimental

alidation of ,a! su!!orted tube subected to

fluid-elastic cou!lin, forces for h+brid

characteri'ation tests25 Benmale, "5 Collet, !5 .oltete, "5 $uisse,

Methodol+ for robust roadside safet+ barrier

desi,n and certification a!!lication to steel-

"ood structures

"5 "assen1io, C5 oubel, S5 Ronel, !5 Di0asquale

1;:10 - 1;:30

1=:30 - 1=:.0

$ibrations of a self-e)cited to"er under

turbulent "ind flo" in the !resence of a hi,h

freuenc+ e)citation

'lham %irrou, Lah(en "oni, "ohammedBelhaq

7

e s R o c a r d

&ro!a,ation of deformation and strain "aes in

a tam!in, rammers s!rin,s

*nis +am1a, Sami *yadi, !11edine +ad)-taieb

/ a a - 7 o u M a a

?ain, into account of surface defects in

connections in the d+namics of structures

assembled

Ni(olas 0eyret, ael Che#allier, /ean-Lu( Dion,0ierre *rgoul

1.:.0 - 1=:30

Nonlinear Vibrations

Rhali Benamar :!"', "*;

Material & Structural Dynamics

"arem *rfaoui :!N',N;

offee brea!

0osters session

MD'N" ()*+% *st uro-Mediterranean onference on Structural Dynamics and Vibroacoustics

ednesday, "pril (3, ()*+

14:30 - 1.:10 &lenar+ $99 - Virtual Noise Synthesis b+ !oran Pavic :'NS* Lyon, .R;

Chair< Charles 0é1erat

1.:10 - 1.:.0 &lenar+ $999 - Sound and Vibration .rom .riction 6et#een Soft Materials 7nder Light Loads b+ Adnan A"a# :Bilent ?ni#ersity, urey

Chair< *lain Le Bot


22/455


23/455


24/455

Table of Contents

Tuesday, April 23, 2013 - 10:30 - 12:30

Nonlinear System dynamics I

Vibration pumping of mdof structures using optimised multiple dynamic absorbers, K. Kamel [et al.] .............................1

Effect of electromagnetic actuation on the dynamic of a forced hertzian contact oscillator, A. Bichri [et al.] ....................6

Dynamic friction compact model : a new multicontact tribometer, J. Dion [et al.] ...........................................................10

dynamic simulations of a Bouncing Ball on a randomly vibrating plat form, C. Zouabi [et al.] .......................................16

Free oscillations of a sliding sdof system: effect of a polynomial friction model, F. Majdoub [et al.] ..............................20

Bifurcation-based micro/nano-electromechanical mass detection, V. Nguyen [et al.] .......................................................24

Reduced Order Models in Structural Dynamics and Vibroacoustics I

Reduced-order model for nonlinear dynamical structures having a high modal density in the low-frequency range, A. Batou

[et al.] ..................................................................................................................................................................................28

Wave propagation analysis in porous media via the Wave Finite Element Method, Q. Serra [et al.] ................................32

Application of wave finite element method on reduced models for the analysis of flexural waves in periodic beams, C. Zhou

[et al.] ..................................................................................................................................................................................36

Vibrations of an elastic structure with shunted piezoelectric patches: efficient f.e. formulation and reduced-order models,

L. Pereira da silva [et al.] ...................................................................................................................................................40

Determining sensor locations based on model order reduction techniques, F. Casciati [et al.] .........................................44

ROM for nonlinear vibroacoustic problems with structural and acoustic nonlinearities, Y. Gerges [et al.] ......................47

Smart Materials, Smart Structures and Metacomposites IMounting Vibrational MEMS Energy Harvesters on Printed Circuit Boards for Improved Response, M. Younis [et al.] 51

Experimental investigation on adaptive shunted piezoelectric metacomposites, F. Tateo [et al.] ......................................55

Simple and effective friction compensationonwheeled inverted pendulum systems, B. Strah [et al.] ..............................66

Analytical modeling of an unimorph multi-layer piezoelectric vibration energy harvester, A. Jemai [et al.] ...................70

Vibration reduction of a structure by design and control of a bolted joint, Y. Karim [et al.] .............................................74

Robust Active Vibration Control of Piezoelectric Flexible Structures with Probabilistic Parametric Uncertainty, K. Zhang

[et al.] ..................................................................................................................................................................................78

Dynamics of Machines and Rotating Machinery I

Monitoring bearing defects by acoustic emission: application of empirical mode decomposition method for early detection,

M. Kedadouche [et al.] .......................................................................................................................................................82

On the behavior of the flexible rotor bearing system in the vicinity of the stability threshold, M. Chouchane [et al.] .....84

Application of Modified Modal Assurance Criteria in Mistuning Bladed Disk, P. Wang [et al.] ...................................... 88

Dynamic characteristics of the cyclic-periodic structure with piezoelectric networks, P. Deng [et al.] ............................92

Dynamic analysis of a spur gear with active magnetic bearings in transient regime, B. Slim............................................98

Acoustic reconstruction of the unsteady rotating forces of fan's blade, M. Abid [et al.] .................................................102

Tuesday, April 23, 2013 - 15:50 - 16:30

Poster s I

A method to model beams in dynamic bending under various boundary conditions, T. Ayari [et al.] ............................ 106

I


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Damage monitoring of trust ball bearing by a reliability approach, M. Guemana [et al.] ............................................... 110

Effect of charge polydispersity in the dynamics of a micellar system, L. Talha...............................................................114

Modelling of mechanical behaviour of bogie train, R. Zellagui [et al.] ...........................................................................118

Nonlinear sloshing of two superposed immiscible liquids in a two-dimensional rectangular tank, M. Bachir............... 122

On the waveguide analysis of a helicopter rotor blade by the wave finite element method, C. Droz [et al.] ................. 124Optimization of geometrical parameters ofn covers & hoops of metal packaging boxes, L. Redhouane........................128

Reconstruction of impact force via bayesian approach, A. Khamlichi [et al.] ................................................................ 130

Tuesday, April 23, 2013 - 16:30 - 17:30

Nonlinear System dynamics II

Nonlinear wave propagation in post-buckled structures, A. Spadoni [et al.] .................................................................. 134

Non linear modal analysis of dynamic absorbers, F. Djemal [et al.] ............................................................................... 137

Delayed feedback controller in mems resonators, M. Younis [et al.] .............................................................................. 141

Flow Induced Vibrations and Noise

Turbulent wall pressure measurement in low wavenumber using the flow-induced vibrations, D. Lecoq [et al.] ......... 145

Detecting and Measuring Slug Velocity in Two-Phase Flows Horizontal Pipes, M. Alssayh [et al.] ..............................149

Experimental Investigation of the Equilibrium and Stability of Long Towed Cable Systems, M. Obligado [et al.] ...... 150

Vibration Field Measurements and Force Identification

Model selection for the equation of motion, M. Ruzek [et al.] ........................................................................................154

Determination of forces in risers used in the petroleum industry by indirect measurements, A. Kawano [et al.] .......... 158

Is high-speed digital holography the ultimate tool for vibration analysis ?, J. Poittevin [et al.] ..................................... 162

Dynamics of Machines and Rotating Machinery II

Dynamics of a horizontal axis wind turbine blade under aerodynamic, centrifugal, gyroscopic, and gravity effects, H. Hamdi

[et al.] ............................................................................................................................................................................... 166

Dynamic analysis of spur gear with defected bearings, M. Abbes [et al.] .......................................................................170

Wednesday, April 24, 2013 - 10:30 - 12:30

Material & Structural Dynamics I

Increasing the Modal Overlap Factor of a Beam Using the Acoustic Black Hole Effect, V. Denis [et al.] ..................... 174

Scattering of flexural waves from an acoustic black hole in an infinite thin plate, O. Aklouche [et al.] ........................ 178

Fea nalysis of in-plane shear stresses of a preloded sandwich plate with a viscoelastic core ? application to the disk brake

systems, M. Soula [et al.] .................................................................................................................................................182

Wideband frequency characterization of a shape memory polymer, P. Butaud [et al.] ................................................... 186

Estimation of structural damping using an expansion in the chebyshev orthogonal basis, C. Chochol [et al.] .............. 190

Guided wave propagation in uncertain elastic media through stochastic diffusion matrix, F. Bouchoucha [et al.] ........194

Computational Methods in Vibroacoustics and Mid-Frequency I

Finite element modelling of Poroelastic-acoustic coupled problem, W. Larbi [et al.] .................................................... 210

Prediction of random vibration and acoustic Responses by compression of the statistical Dynamical information of fem

II


26/455

models, G. Borello............................................................................................................................................................ 214

Statistical energy analysis: correlation between diffuse field and energy equipartition, T. Lafont [et al.] ......................218

A new model of improving the transmission loss of aluminium profile with corrugated cores, S. Ouyang [et al.] ........222

On the thermoacoustic properties of aerospace layered structures, D. Chronopoulos [et al.] .........................................223

Quantification of the power injected by acoustic sources inside a complex cavity, F. Ayme [et al.] .............................. 227

Wednesday, April 24, 2013 - 10:30 - 11:30

Nonlinear System dynamics III

Bifurcation Behavior in Switching Converters Driving Other Downstream Converters in DC Distributed Power Systems

Applications, A. El aroudi [et al.] .................................................................................................................................... 198

Chaos Control by Time-Delayed Feedback: Observing Global Properties in Electronic Circuits, H. Benner [et al.] .... 202

Nonlinear Dynamics of A Piecewise Linear Energy Harvesting System, A. El aroudi [et al.] ....................................... 206

Wednesday, April 24, 2013 - 10:30 - 12:10

Smart Materials, Smart Structures and Metacomposites II

Elastic metamaterials with local resonances for broad band vibration isolation, G. Yan [et al.] .....................................231

Dielectric elastomer as active material in membranes for vibration-based enrgy harvesting, E. Zaouali [et al.] ........... 235

On the radiation efficiency of local resonance stop bands, C. Claeys [et al.] ..................................................................239

Electroacoustic metamaterials with negative acoustic properties, H. Lissek................................................................... 243

Sensitivity analysis and control of a cantilever beam by means of a shunted piezoelectric patch, G. Matten [et al.] .... 247

Wednesday, April 24, 2013 - 11:30 - 12:30 Nonlinear Vibrations I

Effects of constraints and stability coefficients on convergence of pso based algorithm for impact localization, A. El-bakari

[et al.] ............................................................................................................................................................................... 252

Non-linear Free Vibration Analysis of Circular Functionally Graded Plates using a Homogenization Procedure., R. El kaak

[et al.] ............................................................................................................................................................................... 256

Dynamic of a squeeze film between smooth lip seal and rough shaft, M. El gadari [et al.] ........................................... 260

Wednesday, April 24, 2013 - 15:50 - 16:30

Poster s II

Detecting dmage in mindlin plates by using the modal strain energy method, F. El khannoussi [et al.] ........................ 264

Effect of porosity on the propagation velocities of ultrasonic waves in the trabecular bone, A. Bennamane [et al.] ..... 268

Elastic wave scattering by periodic cavities in backing material for ultrasound transducers, G. Bai [et al.] ..................269

Experimental ajustement in real time of a semi-active numerical model suspension with a magnetorheological damper, B.

Said [et al.] .......................................................................................................................................................................273

Geometrically non-linear free vibration of c-ss-c-ss symmetrically laminated as4/apc2 rectangular composite plates, O.

Baho [et al.] ......................................................................................................................................................................277

Multi-objective optimization of rail vehicle design moving in curved tracks with relatively high speed, M. Nejlaoui [et al.]

...........................................................................................................................................................................................281

Non-linear free vibrations of c?c?ss?ss symmetrically laminated carbon fiber reinforced peek (as4/apc2) rectangular

composite plates, Z. Zergoune [et al.] ..............................................................................................................................287

III


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Study of mechanical behavior and reliability analysis of the overhead power cables for low voltage dedicated to distribution

network, A. Chouairi [et al.] ............................................................................................................................................ 291

Wednesday, April 24, 2013 - 16:30 - 17:10

Material & Structural Dynamics II

Propagation of deformation and strain waves in a tamping rammers springs, A. Hamza [et al.] ....................................295

Methodoly for robust roadside safety barrier design and certification application to steel-wood structures, M. Massenzio

[et al.] ............................................................................................................................................................................... 299

Wednesday, April 24, 2013 - 16:30 - 17:50

Friction Noise

Friction noise of rough surfaces and dissipation of vibration, A. Le bot [et al.] ............................................................. 303

Characterization of hysteretic friction of viscoelastic joints, H. Jrad [et al.] ...................................................................307

Comprehension of friction law instability: application to wiper blade squeal noise, F. Dalzin [et al.] ...........................312

Direct numerical simulation of friction noise, H. Dang [et al.] ....................................................................................... 317

Wednesday, April 24, 2013 - 16:30 - 17:30

Nonlinear Vibrations II

Vibrations of a self-excited tower under turbulent wind flow in the presence of a high frequency excitation, I. Kirrou [et

al.] .................................................................................................................................................................................... 321

Numerical simulation and experimental validation of gap supported tube subjected to fluid-elastic coupling forces for hybrid

characterization tests, W. Benmalek................................................................................................................................. 325

Taking into account of surface defects in connections in the dynamics of structures assembled, N. Peyret [et al.] .......329

Thursday, April 25, 2013 - 10:10 - 12:10

Computational Methods in Vibroacoustics and Mid-Frequency II

The Wave Based Method: current state of the art, E. Deckers [et al.] .............................................................................333

Non resonant contributions in modal energy methods, N. Totaro [et al.] ........................................................................337

Dynamics of stochastic and periodic structures in mid-frequency range, M. Ben souf [et al.] .......................................341

SAMSARA for thin stiffened shells: first models, S. De rosa [et al.] ............................................................................. 345

A new approach in reliability based design optimization of Tuned Mass Damper in seismic vibration control of structures

with bounded uncertain parameters, E. Mrabet [et al.] ....................................................................................................349

Detection of localized damage in rails by using elastic wave propagation, S. Teidj [et al.] ............................................353

Materials for Vibroacoustics I

Methodology using a Heat Regulated Impedance Tube for the Temperature Dependent Sound Absorption Property of

Materials, N. Merlette [et al.] ...........................................................................................................................................357

Acoustics of rigid porous media with damped Helmholtz resonators, C. Boutin.............................................................361

Acoustic impedance of microperforated honeycomb panels, M. Regniez [et al.] ...........................................................364

An analytic study of the noise reduction of an infinite multi-layered cylinder, J. Magniez [et al.] ................................ 368

The transmission loss of sandwich-composite panels with attached noise control materials, H. Osman [et al.] ............372

Design of an Acoustic Anechoic Chamber for Application in Teaching Aid, R. Youcef..................................................373

IV


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Robust Design under lack of knowledge

On the modeling of adhesive contact and stiction failure in micro-switches, L. Wu [et al.] ...........................................377

Sensitivity Anlysis and Optimization of Sheet Steel Thickness for Vibroacoustic Behavior of Enclosures, T. Fourmaux [et

al.] .................................................................................................................................................................................... 381Optimum shape design of incompressible hyperelastic structures with analytical sensitivity analysis, A. Jarraya [et al.] ....

385

Robust model calibration of a wind turbine with load uncertainties, D. Pereiro [et al.] ................................................. 389

Robust design of spacecraft structures under lacks of knowledge, F. Maugan [et al.] .................................................... 393

Real-time and in-service estimation of the degree of damage of automotive transmission parts with the aid of a torque

measure, S. Foulard [et al.] .............................................................................................................................................. 397

Thursday, April 25, 2013 - 10:10 - 11:50

Nonlinear Vibrations III

Theory and applications of the macroscopic quantization effect in nonlinearly-coupled vibrating systems, J. Tennenbaum

[et al.] ............................................................................................................................................................................... 401

Non-linear dynamic behavior of a wind turbine system with torque limiter, K. Abboudi [et al.] ...................................405

Effect of high-frequency ac electromagnetic actuation on the dynamic of an excited cantilever beam, A. Bichri [et al.] ....

410

Internal resonances in nonlinear nanocantilever arrays under electrostatic actuation, S. Souayeh [et al.] ..................... 414

Transverses linear vibration of cantilever beam carrying two lumped masses. Analogy between discrete models., A.

Eddanguir [et al.] ............................................................................................................................................................. 418

V


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MEDYNA 2013: 1st Euro-Mediterranean Conference 23-25 Apr 2013

on Structural Dynamics and Vibroacoustics Marrakech (Morocco)

Vibration pumping of mdof structures using optimised multiple

dynamic absorbers

K. Khelifi1, M.-L. Bouazizi1*, R. Nasri2, N. Bouhaddi 3

1Preparatory Engineering Institute of Nabeul (IPEIN), Nabeul- Tunisia

[email protected] and [email protected]

2National School of Engineers of Tunis (ENIT), Tunis- Tunisia

Rachid.Nasri @ enit.rnu.tn3FEMTO-ST Institute UMR 6174, Applied Mechanics Department, University of

Franche-Comté – France :[email protected]

ABSTRACT

The concept of energy pumping is an innovative dynamic phenomenon; it gives rise to new

generation of dynamic absorbers. Theoretical studies and feasibility tests are necessary for

better understanding of their dynamic behaviour and to be applied on real structures or

machines.

In this paper, numerical evidence is firstly given for the passive and broadband targeted

energy transfer in the case of a linear system under shock excitation with Multiple Dynamic

Absorbers or Nonlinear Energy Sink (NES). Secondly, it is shown that many NES absorb

shock energy in only way and dissipate this energy locally, without “spreading” it returns tothe linear system. The numerical results of optimisation in the case of NES linked to a linear

beam are compared to Tuned Mass Dampers (TMD) linked to the same beam.

Keywords: Energy pumping, dynamic absorber, Cubic non-linearity, nonlinear energy sink, tuned

mass damper, Optimisation.

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MEDYNA 2013 23-25 Apr 2013, Marrakech (Morocco)

2

1 INTRODUCTION

The phenomenon of energy pumping is an irreversible transfer of energy from a main structure to

a secondary structure, as dynamic absorbers called nonlinear Energy Sink (NES) are linked to the

main structure. In previous works [1-3], it has been shown that essentially nonlinear oscillators

attached to linear discrete structures that act as broadband passive absorbers of vibration energy.Particularly, it has been shown that transient resonance captures of the transient dynamics may

initiate one way, irreversible targeted energy transfer from a linear (main) subsystem to a local

essentially nonlinear attachment, which acts, in essence, as nonlinear energy sink (NES). In this

work, we propose to optimise the portion of energy damped by the linear and nonlinear dampers

linked separately to a beam. The design parameters to optimise are mass ratio, linear and

nonlinear stiffness and damping ratio of the dynamic absorbers. For this multi-objective

optimisation we calculate the Pareto solutions using NSGA algorithm (Non-dominated Sorting

Genetic Algorithm) [4, 5].

2 DYNAMIC EQUATIONS OF MOTION OF MDOF SIMPLY SUPPORTED BEAM

The studied structure consists of an impulsively forced simply supported damped linear beam,

comporting multiple dynamic absorbers (Figure 1). This system was introduced in [1] with only

one NES.

Figure 1. Simply supported beam with Multiple Dynamic Absorbers

The beam finite element model is based on the Euler-Bernoulli theory.

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&&&

&

λ

δ δ λ ρ λ

(1)

The finite element model for the beam with NES is written as follow:( ) ( ) ( ) ( ) ( ) My t By t K y y t F t + + =&& & (2)

Where , M K and B are respectively the mass, stiffness and damping matrix.

The energy dissipated by the NES and the TMD at time t is defined by the ratio:

( ) ( )

( )

( ) ( )∫

∫∑

=

=

=

==T

a x

t n

i

d xi

inj

TMD NES

d F

d

E

t E t

i

0

0 1

2

/

v

y-v

τ τ

τ λ

η

&

&&

(5)

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3

Where F , iλ , v& and y& represent respectively the impulse force, damping ratio and the velocity at

i x d = ( location of the NES and TMD).

3 OPTIMISATION STUDY

In this section, we propose the multi-objective optimisation of the linear and nonlinear dynamic

dampers (TMD, NES). The NSGA genetic algorithm is used to explore the design space and

exploit the whole solution of the Pareto front [4]. For this study the multi-objective optimisation is

defined in the following form:

[ ]

1

( 1) , , , 1, 2 , .. .

( 2 )

i i i i

n

i

i

M a x F w h ere x m k C i n

x

m

M in F M

x

η λ

=

= ∈ =

=

∑ (6)

Where , , ,i i i im k C λ are the coefficient of the mass, damping and stiffness of the TMD or the NES;

M is the primary structure mass.

3.1

Optimisation of the beam with two TMD

In the first case of this optimisation, we consider the beam defined in section2. The parameters of

the two TMD are identical: 327.215 / k N m= , 0.3m kg= and 0.057 . / N s mλ = . These TMD

are coupled in the beam at location ( 1 0.25d m= and 2 0.8d m= ). The variation levels of the

design parameters are 20% for ( ,m k ) and 90% forλ . As a results the maximum of the 1F is

89.04% for the minimum of 2 0.4F kg≤ corresponding to the design

parameters3

21.7720 / ,opt k N m=

0.2926opt m kg= and 0.1083 . / opt N s mλ = . Then, we examine the influence of variation of the

optimum values of stiffness and damping ratio. The figure2 illustrates this variation. We note that

a variation of 3% of opt k and opt λ leads to a variation of 0.03% of 1F . This low variation shows

that the optimal Cost-Function is robust to dissipate the vibration energy of the beam

21 21.5 22 22.50.8904

0.8905

0.8905

0.8906

0.8906

0.8907

0.8907

0.8908

0.8908

Stiffness

D a m p e d e n e r g y i n t w o T M D

0.104 0.106 0.108 0.11 0.112 0.114

0.8902

0.8902

0.8902

0.8902

0.8902

0.8902

Damping ratio


(a) (b)

Figure 2. Variation of dissipated energy ratio in two TMD: – (a) variation of stiffness – (b)

variation of damping ratio

Finally, we examined the efficiency of the two TMD to dissipate the energy with different

locations d before and after optimisation. Figure3a shows this variation, we note that the energy

ratio absorbed by the two TMD before optimisation is 89%η = and after optimisation it becomes

78%η = at two locations of TMD : 0.2d m= and 0.8d m= .

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4

0 0.2 0.4 0.6 0.8 10.5

0.6

0.7

0.8

0.9

1

X-position


before optimization

after optimization

0 0.2 0.4 0.6 0.8 10.4

0.5

0.6

0.7

0.8

0.9

1

X-position

D a m p e d e n e r g y i n t w o N E S

before optimization

after optimization

a- Dissipated energy versus X-position (TMD

case)

b- Dissipated energy versus X-position (NES

case) Figure 3 : Dissipated energy with optimised dynamic absorbers

3.2 Optimization of the beam with two NES

In this section, we consider the same beam with a two NES at different locations (Fig.1). The

following parameters of the two NES are identical:

3

1 2 1322 / C C C N m= = = ,1 2 0.1m m m kg= = = and 1 2 0.05 / Ns mλ λ λ = = = . We consider the same variation levels of the

design parameters defined in the previous section except that the variation of C is 50% . As a

results, the maximum of 1F is 95% for 2 0.2F kg= and the optimum value obtained by

optimisation of design parameters are: 31983 / opt

C N m= , 0.08opt m kg= and 0.095 / opt Ns mλ = .

Now, we examine the robustness of the optimum values ( ,opt opt C λ ) by variation of 3%. We note

that the variation ofopt C and opt λ for this percentage (3%) causes a small variation of 0.04% of

the cost-function1F . So, these optimum values are robust to dissipate the maximum of energy

from the beam. Then, we examine the efficiency of two NES to dissipate the shock energy before

and after optimisation by varying its location on the beam. Figure3b illustrates the energy ratiodissipated by two NES for different positions on the beam. We note that this ratio reaches

95.40% after optimisation with two positions 1 0.2d m= and 2 0.8d m= , whereas before

optimisation this ratio is 91%η = . As a conclusion, the variation of the position of the two NES

affects its efficiency on the middle of the beam and we note that the two NES design are more

efficient than two TMD design.

4 CONCLUSION

In this paper, we present a multi-objective optimisation of the dynamic absorbers (TMD and

NES). In the first step of optimisation, we consider beam with two TMD the dissipated energyratio after optimisation is 85%. On the other hand, this ratio reached 95% in the case of the beam

with two NES. The robustness study with two TMD and two NES shows that the variation of the

design parameters around the optimal values does not affect the dissipated energy ratio. Finally,

the variation of the position of the two TMD and two NES affects its efficiency on the middle of

the beam.

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5

REFERENCES

[1] Georgiades F., Vakakis A.F., Dynamics of a linear beam with an attached local nonlinear energy sink,

Communications in Nonlinear Science and Numerical Simulation 12 (2007) 643–651.

[2] Vakakis A.F., Manevitch L.I., Gendelman O., Bergman L., Dynamics of linear discrete systems

connected to local,essentially non-linear attachments, Journal of Sound and Vibration 264 (2003) 559–577.

[3] Vakakis A. F., Rand R.H., Non-linear dynamics of a system of coupled oscillators with essential

stiffness non-linearities, International Journal of Non-Linear Mechanics 39 (2004) 1079 – 1091.

[4] Bouazizi M.L., Ghanmi S., Nasri R., Bouhaddi N. , Robust optimisation of the non-linear behaviour of

a vibrating system, European Journal of Mechanics A/Solids 28 (2009) 141–154.

[5] Bouazizi M.L., Ghanmi S., Bouhaddi N., Multi-objective optimization in dynamics of the structures

with nonlinear behaviour: Contributions of the metamodels, Finite Elements in Analysis and Design 45

(2009) 612 – 623.

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MEDYNA 2013: 1st Euro-Mediterranean Conference

on Structural Dynamics and Vibroacoustics

23-25 Apr 2013

Marrakech (Morocco)

EFFECT OF ELECTROMAGNETIC ACTUATION ON THE

DYNAMIC OF A FORCED HERTZIAN CONTACT

OSCILLATOR

A. Bichri and M. Belhaq

Laboratory of MechanicsUniversity Hassan II-Casablanca, Morocco

Email: [email protected], [email protected]

ABSTRACT

The effect of electromagnetic actuation (EMA) on vibroimpact dynamic in a single-sided Hertzian

contact forced oscillator is investigated analytically and numerically near primary resonance.

Attention is directed toward the case where the frequency of the alternative driven current inthe EMA is assumed to be fast with respect to the frequency of the basic vertical harmonic load.

An averaging technique based on the direct partition of motion (DPM) is first performed over

the fast motion to derive the equation of the slow dynamic and then a perturbation analysis

is applied on the slow dynamic to obtain the corresponding frequency response curves. It is

shown that an EMA has an influence on the frequency shift in the case of DC actuation and on

both the frequency shift and the nonlinear characteristic of the response in the case of fast AC

actuation.

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1 INTRODUCTION

Hertzian contacts are present in various mechanical devices and arise in many engineering ap-

plications, especially in mechanisms transforming movement of rotations or translations. A

simple system to investigate this behavior is a moving surface subjected to a Hertzian contact

force modeled by a single degree of freedom system. In [1], the vibroimpact dynamic of sucha problem was studied numerically, analytically and using experimental tests in the case of a

sphere-plane contact excited by a normal static and harmonic loadd. It was concluded that con-

tact losses are provoked by jump phenomena near resonances.

The present work aims at investigating analytically and numerically the influence of EMA on

the nonlinear characteristic of the frequency response and on the location of jumps near the

primary resonance in a Hertzian contact oscillator. The purpose is to assess the possibility of

tuning the resonance frequency values of the system by using EMA with a DC actuation or with

a fast harmonic AC actuation.

2 CASE OF EMA WITH DC ACTUATION

We analyze the effect of EMA with a DC actuation on the frequency response of a forced single-

sided Hertzian contact system. The schematic model of the system is shown in Fig. 1 and the

equation of motion can be written in the form

mδ̈ + cδ̇ + kδ 3/2 = N (1 + σ cos νt) + F em (1)

The electromagnetic force F em is given by

F em = C 0I

2

(e− δ )2

(2)

and I is the current induced in the magnetic circuit of the EMA which is supposed to be constantsuch that I = I 0.

Figure 1: Schematic model of forced single-sided Hertzian contact oscillator submitted to EMA

Equation (1) can be rewritten in the following dimensionless form

z

+ αz

+ (2

3z + 1)3/2 = 1 + σ cosωτ +

a0

(R− 23z )2

(3)

where δ = δ s(23z + 1), δ s = (N k )

2/3, ω20 = 3k2mδ

1/2s , τ = ω0t, ω = ν ω0 , α = cmω0

, a0 = 3C 0I

2

0

2mω20δ3s

and

R = e−δsδs

. The nonlinear terms of Eq. (3) can be approximated using Taylor series expansion.

2

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Expending these temes keeping only terms up to order 3 leads to

z

+ αz

+ ω21z + β 1z

2 − γ 1z 3 + G1 = σ cosωτ (4)

where ω21

= 1− 4a0R−3

3 , β 1 = β − 4a0R

−4

3 , γ 1 = γ +

32a0R−5

27 , G1 = −a0R−2, β = 16 and γ =

1

54.

Using the MMS [2], we obtain the following amplitude-frequency-response equation

C 21r6 + 2B1C 1r

4 + (A21 + B2

1)r2 − (H 2

1 + H 2

2) = 0 (5)

Figure 2 depicts the frequency-response curve for two different values of a0 (which is related tothe current I 0).

Figure 2: Amplitude-frequency response near the primary resonance. (a): a0 = 0, (b): a0 =0.07; α = 0.02, σ = 0.03 and R = 1. Analytical approximation (solid lines for stable anddashed lines for unstable), numerical simulation (circles).

3 CASE OF EMA WITH DC AND A FAST AC ACTUATIONS

In this section we consider that the rigid mass is excited by two EMAs, as shown in Fig. 3. The

first EMA applied from above is actuated with DC debited by the current I 1 while the secondactuator is actuated from below and produces AC actuation in the form I = I 0 cos κt, where I 0and κ are, respectively, the intensity and the frequency of the excitation.

Figure 3: Schematic model of forced single-sided Hertzian contact oscillator submitted to twoEMAs actuation.

Assume that the current I 1 is imposed according to the relation

I 1 = I 0(e + δ )√

2(e− δ )(6)

3

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the dimensionless equation of motion takes the form

z

+αz

+ z + βz 2− γz 3 = σ cosωτ + a0(R−2 + 4

3R−3z +

4

3R−4z 2 +

32

27R−5z 3)cosΩτ (7)

We use the method of DPM [3], we find the approximate equation of the slow dynamic

x

+ αx

+ ω21x + β 1x

2 − γ 1x3 + G1 = σ cosωτ (8)

in which the parameters are now given by ω21

= 1 + 20a2

0R−6

9Ω2 , β 1 = β +

40a20R−7

9Ω2 , G1 =

2a20R−5

3Ω2

and γ 1 = γ −400a2

0R−8

81Ω2 . Here we use the same frequency-response equation (5) obtained in the

previous section but with the new definition of parameters as given in (8).

Figure 4 illustrates the frequency-response curves for different values of a0.

Figure 4: Frequency response near primary resonance for α = 0.02, σ = 0.03, Ω = 8 andR = 1. Analytical approximation (solid lines for stable and dashed lines for unstable).

4 CONCLUSION

We have studied analytically and numerically the effect of a fast harmonic EMA on vibroimpact

dynamic in a single-sided Hertzian contact forced oscillator near the primary resonance. The

method of DPM was applied to obtain the main equation of the slow dynamic and the MMS

was implemented for obtaining the frequency response of the slow dynamic near the resonance.

It is shown that adapted EMAs with DC and AC actuations not only produce a shift of the

frequency response to the right, but also a change of the nonlinear characteristic of the system is

obtained. Specifically, fast EMA actuation as suggested in the present study shifts the frequency

response right (not left as in the case where only DC actuation is present) and changes the

behavior of the system from softening.

REFERENCES

[1] J. Perret-Liaudet, E. Rigaud. ”Response of an impacting Hertzian contact to an order-2

subharmonic excitation : Theory and experiments”. Journal of Sound and Vibration, 296:

319-333, 2006.

[2] A.H. Nayfeh, D.T. Mook. ”Nonlinear Oscillations”. Wiley: New York.

[3] I.I. Blekhman. ”Vibrational Mechanics - Nonlinear Dynamic Effects, General Approach,

Application”. Singapore: World Scientific, 2000.

4

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MEDYNA 2013: 1st Euro-Mediterranean Conference 23-25 Apr 2013

on Structural Dynamics and Vibroacoustics Marrakech (Morocco)

DYNAMIC FRICTION COMPACT MODEL :

A NEW MULTICONTACT TRIBOMETER

J.L.DION, G.CHEVALLIER, O.PENAS, F.RENAUD1Lab or Company Name

LISMMA- EA 2336

SUPMECA - 3 rue Fernand Hainaut 93407 Saint Ouen Cedex

France

[email protected]

ABSTRACT

This paper presents an original friction measurement setup. It is designed to uncouple normal and

tangential load. Friction measures acquired with this setup present a high signal to noise ratio.

This friction experimental device allows characterizing various types of surfaces and several

levels of excitation from static strain to dynamical motion including micro-sliding and macro-

sliding. A measurement example is presented for a contact pair of Aluminum alloy starting from

sticking limit until complete sliding. Finally, in order to use the results in vibration reduced

models, a method is proposed to identify the compact Lugre Model from these measurements.

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MEDYNA 2013

1 DESCRIPTION

Many previous works use

bench allow to uncouple

ensure the good quality ofto verify this assumption a

relative displacement and s

and with a great accuracy.

System 830 which allows

[1.2-120] mm/s velocity r

composed of three orthogo

3). Each symmetry-plane a

tangential forces (plane P

tribometer, is iso-static. Th

hydraulic machine but the

and avoids hyperstatism i

performed with a flexible

planes P1 and P2. Moreov

screw are symmetric on bo

symmetry for three orthog

and for load distributions.

Figure 1: Principle of co

symmetry-planes (P1, P2 a

an eq

23-25 Apr 2013,

2

r have developed tribometers ([1-11], [16-21]

ormal and tangential loads over a wide freq

measurements and test conditions, as previousd to identify state and rate models, normal fo

liding velocity have to be measured over a la

Our tribometer has been so mounted on a

to obtain at 200 Hz a [1-100] µm displacem

nge. To decouple normal and tangential lo

nal symmetry-planes with four contact areas (

llows an equal repartition of normal forces (

). The complete experimental set, compose

base sample (Figure 1) is clamped on the re

obile sample is free in rotation around the ja

the mechanism. For the same reason, the

screw. The axis of this screw is placed alon

er, the two application points of the normal

h sides of P3. These technical choices allow t

nal planes, both for geometric properties of t

tact areas and normal and tangential forces Th

nd P3) allow decoupling between normal and t

al repartition of these forces on each sample.

arrakech (Morocco)

) The proposed test

uency bandwidth to

ly exposed. In orderce, tangential force,

rge frequency range

TS Elastomer Test

nt range inducing a

d, the test setup is

Figure 1 and Figure

lanes P1 & P2) and

of samples in the

ference frame of the

k displacement axis

ormal force (N) is

the intersection of

orce applied by the

assume a satisfying

e mechanical setup

three orthogonal

angential forces and

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MEDYNA 2013

During the test, with tang

However the normal load i

during the test. This assu

attention has been paid in

normal and tangential load.

For all the tests, hydraulic

signal of the internal displa

force sensors (Fn, Ft, Ft2), 1

(xm, xh, xb) and 2 accel

assumptions, only 3 sensors

(Ft, Fn) and 1 displacement

Figure 2:

3 COMPACT MODEL SE

Many compact models have al

LuGre model [14] can be consfriction factor introduced by t

model was completed in 2002

slipping limit has been reached.

23-25 Apr 2013,

3

ential motion, static normal load is assum

s always measured and controlled with high

ption is often not verified on other tribo

he design of this tribometer in order to avoi

jack movements are displacement controlled

cement transducer (LVDT). Measurements a

LVDT displacement sensor (X), 3 Foucault

rometers (Ae, Af). Most of them are used

are necessary for dynamic friction measurem

LVDT (X).

Schema and partial picture of the tribometer.

ECTION AND PARAMETRIC IDENTIFI

ready been developed in previous works ([12]

idered as an evolution of Dahl’s model withe “g” function, often chosen as a Gaussian f

[12] and it includes elastoplastic behavior th

( )

( )

0 0 1

0( )

( ) s

t n

x

V

d s d

F K z C z C x F

xdz x K z

dt g x

g x e

α

µ µ µ

−

= + +

= −

= + −

ɺ

ɺɺ

ɺɺ

ɺ

ɺ

arrakech (Morocco)

d to remain static.

frequency sampling

eters. A particular

d coupling between

with the feed-back

e performed with 3

isplacement sensors

in order to verify

nt : 2 force sensors

CATION

-[15], [22-29]). The

velocity dependantunction. The LuGre

at occurs before the

(1)

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4

The proposed identification method is robust and has been applied for a very large number of tests

with several frequencies and normal loads. The quality of fitting between simulation and

measurements in Figure 3 is similar for most of the tests; some are better while only a few (less

than 5%) are worse.

Figure 3: Comparison between measurement and simulation obtained with the proposed

identification method

2 CONCLUSION

This work was performed in the field of structural vibrations. In a complex mechanism, the

level of vibration strongly depends on the dissipation in the connected parts. This work

presents a new test bench designed for improving the accuracy of measurements of non linear

dissipative behaviors of frictional interfaces. This test bench is used for dynamic friction

studies. Magnitudes of displacement have been tested from 10-5

m to 10-2

m while those of

velocity have been studied from 10-7

m/s to 10 m/s. The tribometer design allows a very good

independence between normal and tangential forces. Measurement techniques and signal

processing methods highlight excellent accuracy with both direct measurements and

parametric identification. As an illustration and because it is very well-formulated for

vibrations problems, the LuGre Model has been identified from experimental results. An

accurate method for parametric identification has been performed and a rheological

description of the LuGre model has been presented. The prospects for improvement of this

test means are to enable the measurements of the dissipative behavior on the scale of

roughness. Thus the next test bench should make it possible to obtain measurements ofdisplacements under 10

-7m.

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5

REFERENCES

[1] Chevallier G., « Etude des vibrations de broutement provoquées par le frottement sec -

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