1st euro-mediterranean conference on structural dynamics and vibroacoustics, medyna2013 -...
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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.
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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.
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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.
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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
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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
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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
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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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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.
( ) ( ) ( )( ) ( )[ ]
( )( ) ( ) ( ) ( )
( )[ ] ( ) ( )
==
∂∂−+−+
−=
−
−
∂
∂+−+
∂
∂+
∂
∂+
∂
∂∑
=
nit
t d yt t d yt C t m
a xt F d xt t
t d yt t d yC
t
t x y A
t
t x y
x
t x y EI
iiiii
n
i
i
i
iii
......2,10,v,)(v)(v
v,
v,,,,
i3
ii
1
i
3
i2
2
4
4
&&&
&
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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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
D a m p e d e n e r g y i n t w o T M D
(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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0 0.2 0.4 0.6 0.8 10.5
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 T M D
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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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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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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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
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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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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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 -
application a