active structures and noise control technical group · active structures and noise control...
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Active Structures and Noise Control Technical Group
2009 CAV Workshop
George Lesieutre Mary Frecker
Christopher Rahn
Aerospace Engineering Mechanical Engineering
The Pennsylvania State University
Updates on the Actuation of Miniature Trailing-Edge
Effectors
Michael Thiel
George A. Lesieutre
Sponsors: U.S. Army, NASA
Miniature Trailing-Edge
Effectors
• Static: Gurney flaps
– Small tab on lower surface of airfoil
– Increase sectional lift coefficient
• Dynamic : Miniature Trailing-Edge Effectors (MiTEs)
– Has potential to increase rotorcraft performance
– Distribute span-wise along rotor blade to delay stall
On/Off Deployment
Optimal deployment (for
greatest increase in lift)
is a square wave
Approximate as a 3-
term (plus offset)
Fourier series
For different duty cycles
– vary the magnitudes
Multi-Degree of Freedom Actuation
Design a piezoelectric (PZT) bimorph with
resonances at harmonics of the square wave
Should require low power and need no motion
amplification – direct drive
Able to design actuator with natural frequencies
at the 1st and 3rd harmonic – but drive voltages
exceeded PZT material limits
Minimization of Power Required
Second study to minimize power to create a 4 Hz square wave
1st natural frequency at the 3rd harmonic
Voltage drive below PZT limit
Built and tested
Fabricated Design
Acquire FRF then adjust magnitude and phase
based on the data
Able to approximate square wave
Drive within material limits
Reduction of High-Cycle Fatigue in Integrally Bladed Rotors
through Piezoelectric Vibration Damping and Control
Jeffrey L. Kauffman
George A. Lesieutre
Sponsor: NASA Glenn Research Center
Damping Motivation & Approach
Integrally bladed rotor (IBR) lifetime reduced by high-cycle fatigue cracks IBRs are single pieces of material with little
damping Increased turbomachinery efficiency
No added damping from friction interfaces
Periodic aerodynamic forcing inherent to turbomachinery (rotor/stator passes)
High-cycle fatigue reduction through piezoelectric vibration damping Passive and/or semi-active damping and control
Hybrid harvesting-switching approach
Significant damping system constraints Implementation in rotating frame
Preservation of aerodynamics & structural integrity
Survival in high temperature environment
Additional modeling concerns High modal density
Complex geometry
–Integrally Bladed Rotor
–Previous turbomachinery
design
Passive Damping
Piezoelectric material shunting Resistive: frequency dependent damping
Inductive: resonant (damped) absorber
Capacitive: frequency dependent stiffness
Each approach employs additional circuitry
Multiple approaches may be needed for damping of multiple modes Single material patch with switching for
several shunt topologies
Semi-active techniques as well
Advanced concepts Resonance frequency de-tuning
Hybrid harvesting-switchingCapacitive Shunt
Resistive Shunt
Implementation Considerations
Piezoelectric material is typically placed in high-strain region
Optimal placement is typically mode-dependent 2-stripe (2S) & 3-bending (3B) modes are current modes of interest
Material placement constrained by turbomachinery environment Embedded piezoelectric material
Composite blades
Initial placement determined by coupling coefficient Measure of total blade energy
conversion (here, strain-to-electrical)
Effects depend on blade rotation
Conclusions & Current State
Piezoelectric vibration damping can significantly enhance IBR lifetime Dramatically reduce high-cycle fatigue in blades
Preserve aerodynamic & structural integrity
Ensure IBR remains efficient & attractive compared to “previous design”
Initial experimental testing completed at NASA Glenn Research Center Resistive, capacitive, and inductive shunts tested
Blade with piezoelectric patch tested in dynamic spin rig Ensure integrity of blade/patch structure
Determine potential impact of shunted patch through coupling coefficient
Initial results show appreciable damping increases
Advanced testing is in progress (throughout May ’09) Resistive and inductive shunts in dynamic spin rig
Simple harvesting concepts in bench-top environment
Beyond specifics of damping system, significant areas of research remain Realistic placement of patches and circuitry
High-temperature materials and coatings
Power & data transfer from rotating frame
Fabrication and Design of Nanoparticulate enabled micro forceps
Team Members: Milton Aguirre, Gregory Hayes, Nick Antolino, Christopher Muhlstein, Becky Kirkpatrick, Donald
Heaney, Eric Mockensturm, Sanjay Joshi, Harriet Black Nembhard, Alan Snyder, James Adair, Dr. Mary Frecker
Departments of:
Materials Science and Engineering
Mechanical and Nuclear Engineering
Industrial Engineering
The Pennsylvania State University, University Park, PA, 16802 USA
Ceramic and Composite Materials CenterAn NSF Industry/University Cooperative Research Center
National Nanotechnology Infrastructure Network
Introduction: Motivation
Flexible Endoscope
Minimally Invasive Surgery: MIS
NOTESTM [4]
NOTESTM => Natural Orifice
Transluminal Endoscopic Surgery
2-3 working channels
ranging in Dia. 1-5 mm
Laparoscopy [1]
1) Eliminate external incisions
2) No cosmetic scaring
3) Shorter hospital stays
4) Decrease risk of infection
5) Reduced recovery pain
Advantages of NOTES
[2][3]
Laparoscopy vs.
Ports
Mold Infiltration
Gel Casting
Planarization
Mold Removal
Sintering
Final Parts
Mold Fabrication
Colloid
Preparation
Gel Casting
Preparation
Mechanical
StrengthPerformance Testing
Project Process Flow Diagram
Instrument Design (FEA)
(1) Mold FabricationUV
MaskUV Filter
SU8 moldAntireflective coatingAl2O3 Substrate
Cross sectional image of forceps mold
As received Tosoh zirconia
powder 60 m by DLS
Chemically Aided Attrition Milling
(CAAM) 3mol% Yttria stabilized Zirconia
Dispersed, CAAM Tosoh
3YSZ powder 45vol%
136nm by DLS
CA
AM
(2) Material Fabrication
(3) Mold Infiltration
Fabrication
The mold is Burned away and ceramic is
sintered in 1 firing cycle run.
(4) Mold Removal and Sintering
TimeTem
p
1400 C for 2 hrs
600 C for 2 hrs
Refractory Al2O3
SU-8 3YSZ SU-8
Refractory Al2O3
3YSZ
Instrument DesignStrength data, collected from Zirconia test bars, is used in an
optimization routine to determine optimal dimensions of the device.
Tool Operation:
As the sheath is
advanced forward, the
forceps arms displace
toward one another
producing a grasping
motion.
Contact Stress Relief:
The forceps design
features a gap to provide
stress relief as contact
occurs between the
forceps arms.
Outer SheathPoint of Contact
Tool Actuation
Finite Model of MesoForceps with
Dimensional Parameters
gap open
L1 L2
L
3
Design Optimization Results
An illustration of contact stress relief,
here contact occurs when the outer
sheath is located 60% along the total
length.
Contact Stress Relief
0
100
200
300
400
500
600
700
0 10 20 30 40 50 60 70
Ma
x. P
rin
cip
al S
tre
ss
(M
Pa
)
Percentage along L2 (%)
allow
Contact
Occurs
Aspect Ratio (L:w) = 45
L:w 13.5 mm: 0.3 mm 1.0 mm
Dia.
0.3 x
0.3 mm
2
m
m
Solid Model Assembly
Performance Plots?
0
5
10
15
20
25
30
35
40
45
50
0 500 1000 1500 2000 2500
As
pec
t R
ati
o (
L:w
)
Ultimate Strength (MPa)
0
1
2
3
4
5
6
7
8
0 500 1000 1500 2000 2500
Fo
rce
(N
)
Ultimate Strength (MPa)
Fabrication Results
Testing Results
x, y, & z axis
piezo-actuator
load cell
PC /
controllerMechanical
bend bar
Knife edge
loading
points
AcknowledgmentsThe Adair Research Group
The Frecker Research Group
PSU Nanofab Staff
Penn State MRI Nanofab: the Pennsylvania State University Materials Research Institute NanoFabrication Network
and the National Science Foundation Cooperative Agreement No. 0335765, National Nanotechnology Infrastructure
Network, with Cornell University.
CCMC Ceramics and Composites Materials Center:
NIH Grant Number R21EB006488 from the National Institute Of Biomedical Imaging And Bioengineering. The content
in this paper is solely the responsibility of the authors and does not necessarily represent the official views of the
National Institute Of Biomedical Imaging And Bioengineering or the National Institutes of Health.
NSF Grant Number IIP0637850
NSF – Penn State Cooperative Center
1. Tufts-New England, M. C., 2007, Laparoscopy: A Proven Alternative,
2. Kantsevoy, S. V., Jagannath, S. B., Niiyama, H., Chung, S. S. C., Cotton, P. B., Gostout, C. J., Hawes, R.
H., Pasricha, P. J., Magee, C. A., Vaughn, C. A., Barlow, D., Shimonaka, H. and Kalloo, A. N., 2005,
"Endoscopic gastrojejunostomy with survival in a porcine model," Gastrointestinal Endoscopy, 62(2), pp.
287-292.
3. Wirral Health Informatics Service, 2004, Acorn - Fundraising for Wiral Hospital NHS Trust,
http://www.helpwirralhospital.nhs.uk/campaigns/campaigns.asp
4. Fujinon, 2007, Fujinon Web Site, http://www.fujinon.co.jp/jp/news/icon/endoscope/eg-530n-h.jpg
References
A Bistable Mechanism for Chord
Extension Morphing Rotors
Terrence Johnson, PhD Candidate A
Mary Frecker, Professor B
Farhan Gandhi, Professor A
A: Dept. of Aerospace Engineering, University Park, PA
B: Dept. of Mechanical and Nuclear Engineering, University Park, PA
Actuation concept: use of bistable arc for chord extension
SparHub
Plate RollerArc
First Stable State
Second Stable State
Expected Chord Increase: 20 – 40 %
New Concept
Living hinge: flexural pivot with minute stiffness (modeled as a pin joint)
living
hinge
First Stable
State
Second
Stable State
livin
g
hin
ge
Types of bistable arcs
Continuous Arc
Continuous Arcs joined by Living Hinge
Does not need energy to hold in state
Expected to require less force to
initiate snap
Simple system
Arc Function
Actuator to the flat plate
Support aerodynamic and inertial loads
New Concept
Arc Benefits
Objective: develop a process to design bistable arcs
(various types) for chord extension in aircraft
Focus: Circular Arcs, Rotorcraft systems
Results
Arc Comparison using Abaqus
Study: Force, Energy vs. Displacement
Continuous arc requires larger snap-through
force and displacement
Results
Study: Snap-Through Load and Displacement vs. Curvature
Curvature , Arc Base
Redline: 23 N
Arc curvature , Snap-Through Load and
Displacement
Continuous Arc w/ living hinge, requires less
snap-through load and displacement
When centripetal load is applied, Snap-Through
Load and Displacement
Both arcs are suitable to support Centri. Load
Contact-aided Compliant
Cellular Mechanisms (C3M)
Vipul Mehta (ME)
Prof. Mary Frecker (ME)
Prof. George A. Lesieutre (AERO)
Background
Most engineering materials have a small elastically recoverable strain.
There is a need for high strain materials
Applications include morphing skin, armor, etc.
Global Hawk and a proposed morphing wing cross-section
Modulus and elastic strain
for various materials1
1 Henry, C., and McKnight, G., “Cellular Variable Stiffness Materials for Ultra-Large Reversible Deformation in Reconfigurable Structures,” in Proc. of SPIE 6170, 2006
0 5 10 15 20 25 300
0.2
0.4
0.6
0.8
1
1.2
1.4
1.6
xglobal (%)
/all
non-contact structure - bending stress
non-contact structure - axial stress
contact-aided structure - bending stress
contact-aided structure - axial stress
stress relief
18% to 27%
contact
Proposed Design
Results
Material StrainCellular structure
without contact
Contact-aided
cellular structure
3 % 18 % 27 %
1682 1927 2655 2755 3155 4082 4200 5391 68820
100
200
300
400
500
600
# of unit cells per unit area (1/m2)
Mass (
g)
Non-contact cells: feasible designs
Contact-aided cells: feasible designs
Non-contact cells: infeasible designs
Contact-aided cells: infeasible designs
Application of cellular structures to morphing skin. As the number of cells per unit area increases the structural mass decreases. In general, contact-aided designs have lower mass. Also there are more feasible designs using contact as compared to non-contact designs
Summary
Cellular structures bearing contact provides a huge elastically recoverable strain; as high as 100% more than the cellular structures without contact and almost 30 times the core material strain.
–1 mmOngoing work involves development of Zirconia based meso–scaled cellular structure to obtain a high strength and high strain material.
Piezoelectric Nano Air Vehicles
Hareesh K. R. Kommepalli, Andrew D. Hirsh, Christopher D. Rahn
Department of Mechanical and Nuclear Engineering
Dr. Srinivas A. Tadigadapa, Kiron Mateti
Department of Electrical Engineering
The Pennsylvania State University, University Park, 16802
T-Beam Actuators
T-beam provides two-axis (+/- in-plane and +/- out-of
plane) bending.
Out-of-plane web actuation used in demonstrator.
Fabricated T-Beams
● Diced device parameters: height, h = 1 mm
web width, b = 0.7 mm
length, L ≈ 19.0 mm
flange width, s = 4.4 mm
flange thickness, t = 167.8, 324.3, 523.5, 719.3 μm
● RIE etched device parameters:
height, h = 100 μm
length, L ≈ 8.0 mm
flange width, s = 6 mm
flange thickness, t = 83 μm
RIE Etched Beam Performance
0 50 100 150 200 250 3000
5
10
15
20
25
VW (V)
wL(
) (
m)
Theory
Experiment
Diced T-Beam Test Cases
Diced T-Beam Experimental Results
Clapping Wing NAV Design Using T-Beams
T-Beams
Pin
Hinges
Wing Rods
Demonstrator Design Evolution: Fuselage and Hinges
First Fuselage
Syringe Hinge Design
Pin Hinge Design
Flex Hinge Design
First Design with Dual Wing Rods
First Designs with Dual Wing Rods and Polymer Wings
Dual Syringe Hinge with Wings
Dual Pin Hinge with Wings
Clapping Wing Tabletop Demonstrator
Dual Pin Hinge with Polymer Wings
Demonstrator Videos
0.5 Hz
16 Hz
Future Design With Independently Actuated Wings
Conclusions
T-Beam piezoelectric actuators provide bimorph
actuation in-plane and out-of-plane.
T-Beam actuators can be fabricated using dicing or
RIE etching.
With four electrodes and +V, ground, and float
combinations, the best displacement configuration can
be determined.
T-Beam actuators can be used in a clapping wing NAV.
Wing motion of 30 degrees was demonstrated.
Future research: Design optimization and lift
measurement.