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Design Approaches for the Joining of Ceramic
Components
ADMACOM WorkshopSeptember 14-15, 2016Brussels, Belgium
Audi AG, Fraunhofer ISC Ceramic Composites, Snecma Propulsion Solide, Schunk Group
Walter Krenkel
Ceramic Materials Engineering (CME)University of Bayreuth Germany
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• Designing with Ceramics: Monolithic versus Composite Ceramics
• Challenges in Joining Monolithic Structural Ceramics
• Strain-compatible Hybrid Metal/Ceramic Structures
• Joining with Ceramic Matrix Composites
Brake Disks
Jacketed Pipes
• Summary
Outline
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Truss bridge made of steel (tensile or compressive stresses in
the bars)
Separation of functions of the different construction elements
Typical arched bridge made of brittle
stones (compressive stresses only)
Limited distance between the supports
because of high side thrust
Different Designs with Ductile and Brittle Materials
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-2,0
0,0
2,0
4,0
6,0
8,0
10,0
12,0
14,0
16,0
18,0
0 200 400 600 800 1000 1200 1400 1600
Temperature [°C]
Co
eff
icie
nt
of
therm
al
exp
an
sio
n
[10
-61/K
]
CMC (n.-ox.): C/C-SiC_XT
CMC (ox.): 720/Mullite ║CMC (ox.): 720/Mullite
CMC (n.-ox.): C/C-SiC_XT ║
Steel: St37
Nickel-base alloy: N06022
Monolithic ZrO2 (3 mol Y2O3)
Coefficent of Thermal Expansion of Ceramics Compared with Steel and Superalloys
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Ceramic Components for Gas Turbines
• Preferred ceramic
materials: SiC and Si3N4
• Prototype development
during the „ceramic fever“
in the 1980/90s
• Preferred components like
combustion chambers and
nozzles as well as hot gas
components like blades,
vanes and liners
• Unsolved problems with
insufficient damage
tolerance, reliability and
problems with the
metal/ceramic joinings
Victor Trefilov et al: Development of High-
Temperature Ceramics for Application in Gas
Turbine Engine Components (ASME, 2003)
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Attachments of Ceramic Blades
Metallic rotor with inserted RBSN blades
Stress distribution in the blade root of a metal/ceramic design
a) Ideal surface contact
b) Line contact
c) Asymmetric line contact
Mark van Roode: German Automotive Ceramic Gas Turbine Development
(ASME, 2002)
David W. Richerson: The Ceramic Gas Turbine – Retrospective,
Current Status and Prognosis (ASME, 2003)
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Integral Design of Automotive Gas Turbine Components
Blisks (Bladed Disks) of HPSN (Daimler) and integral vane rings of RBSN
(MTU) for automotive gas turbines
Mark van Roode: German Automotive Ceramic Gas Turbine Development (ASME, 2002)
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Metal-Ceramic Hybrid Blade Design (MTU)
• Concept of a tie-
rod
• Separation of
functions
• Cooled, load-
bearing cores
(metal)
• Uncooled,
compression-
loaded hollow
blades (SiSiC
ceramic)
W. Krüger et al: Ceramic Gas Turbine
Component Development at MTU (ASME, 2002)
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Compression-Loaded Rotor (Ceramic/CFRP Hybrid Concept)
Compression-loaded
blades (uncooled
monolithic ceramic)
Tensile loaded
outer ring (cooled
CFRP)
Segmented rotor
(monolithic ceramic)
Goal: Avoidance of tensile
stresses within the ceramic
material
• Shrinkage fit of high-strength
CFRP support ring to the
ceramic blades
• CFRP support ring has to be
cooled (cooling fins) and
isolated (from the rotor blades)
• Rotor and rotor blades made
of Si3N4
• Segmented rotor (to reduce
the stress level)
Quelle: DLR-Stuttgart
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Ceramic Tiles in Stationary Gasturbines
Ceramic tiles in an annular combustion chamber (Siemens)
• The liner of the combustion
chamber is exposed to only
low aerodynamic loads
(primarily:
thermomechanical and
corrosive loads)
• Reduced cooling air is
required because of the
ceramic „hot walls“
• Ceramic tiles are based on
alumina and mullite
• Microcracked structure
result in a damage-tolerant
behaviour
• The highest loads occur by
thermal shocks during rapid
coolings
C. Taut et al: Siemens KWU – Experience with Refractory
Ceramics in Stationary Gas Turbines (ASME, 2002)
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Refractory Ceramic Tiles
Segment of the ceramic heat shield (Siemens)
• Segmented design reduces the
thermally induced stresses and
facilitates the replacement of the tiles
• Gaps between the different tiles allow
an unhindered thermal expansion
• Sealing air from the compressor
prevents the penetration of hot gases
into the gaps (efficiency loss)
• Attachment of the tiles by metallic
fasteners in the grooves
Properties of the mixed ceramic:
Density 2.8 – 3.0 g/cm3
Open porosity 18 – 20 %
3 pt-bending strength 9 – 12 MPa (RT)
6 – 8 MPa (1200 °C)
Young‘s modulus 13 – 16 GPa
C. Taut et al: Siemens KWU – Experience with Refractory
Ceramics in Stationary Gas Turbines (ASME, 2002)
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X-38 – Nosecap Attachment
DLR Stuttgart
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Design
• Adjustable metal/ceramic fasteners
• Eight sets of levers on the rear side
of the cap
• Levers made of CMC
• Bearing support made of ODS alloy
DLR Stuttgart
Nosecap Attachment by Strain-Compatible Fastening System
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sleeve Screw
Friction rotor
(C/SiC)
Metallic
Bell
Force-locking
Different expansion
behaviors require large
tolerances
Stresses depending on
temperature
Force- and form-locking
Floaters for radial
expansion compensation
Additional expansion
compensation in
circumferential and axial
direction by slotted sleeves
and springs
Strain-Compatible Design of Ceramic-Metal Joinings in High Performance Brakes
Sleeve
Exploded view of the assembly
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Differential Design Applying In-situ Joining Methods (PIP and LSI Process)
Permanent Ceramic Joints made of SiC
Strength of joint almost identical with substrate strength
PrecursorPaste
C-Fabric, Felt
Joining MaterialC-Powder
Joining Material
Paste (80% Precursor / 20% C-Powder)
Optional: One Layer C-Fabric
C/C-Preparation Machining with diamond tools
Curing 135°C / 90 min / air
Siliconization 1500°C / Vacuum
Chemical Reaction: Si liquid + C solid SiC solid
Stringer/Panel + Joining Material Complex Structures
Joining Area
Detail A
Detail A
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Modular Design (Separate Manufacture of Fricion Layer and Load-Bearing Body)
Reibring
Kreissegmente
Friction ring
Friction ring
Core material (e.g. cooling ribs)
Assembly in the
carbon/carbon stage
Process-integrated joining
(reaction-bonding)
Friction ring: High COF, low wear
Core material: High strength, high thermal
conductivity and heat capacity
Separation of functions
C/SiC brake disk
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Form-locking joining between cooling ducts and friction surface
Functions of friction surfaces and load-bearing body are separated
Design studies and prototypes manufactured by DLR already in the 1990s
Internally Ventilated Brake Disks in Modular Design
DLR, Stuttgart
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Wheel Brake Disk ( 750 mm) for High Speed Trains
W. Krenkel: Hochleistungsbremsen aus Faserkeramiken,
MATERIALICA 1998
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Concept of Hybrid Ceramic/Metal Pipes (Jacketed Pipes)
Separation of Functions
• Metal pipe
Assures gas tightness and sufficient corrosion
resistance against steam oxidation
• Interphase
Compensates the tolerances of manufacturing
between metallic pipe and ceramic reinforcement
• CMC reinforcement (jacket)
Takes partially the mechanical and thermal
loads and prevents the metal pipe from creep
High mismatch of the coefficient of
thermal expansion (steel – CMC)
Steel limits the manufacture temperature
of the CMC pipe to 700 °C due to the required
on-site manufacture
© Fraunhofer HTL
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FE Simulations : Model and Variations
• FE software: ANSYS Mechanical
2D model:
– Two coaxial quarters of pipes
– Steel: inner diameter 30 mm, thickness 2 mm
– CMC: UD material C/SiC (hoop-wound)
• Loads/test conditions:
– Inner metal surface: 300 bar
– Over-all temperature: 700 °C
• Variations (pressure and temperature
are constant)
– Wall thickness ratio:
– Young’s modulus of the CMC reinforcement
– CTE of the CMC reinforcement
• Time-dependent simulation
– Gap between steel and ceramic jacket
CMC
steel
pressure
| tS|tC|
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Variation of the Young’s Modulus of the CMC pipe (ratio of wall thickness 1:1, no
gap)
steel only
E|| 75 GPa, E 7 GPa
E|| 150 GPa, E 14 GPa
E|| 187,5 GPa, E 17,5 GPa
Higher stiffness of the CMC jacket leads to higher stresses
in the steel (compressive stresses) and CMC pipes (tensile
stresses)
FE Simulations – Hoop Stress: Influence of Young’s Modulus of the CMC
Ho
op
str
es
s
All results are normed to the value of
the inner hoop stress of the steel pipe
1 2
3 4
steel CMC
1 2 3 4
Bru
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Variation of the coefficient of thermal expansion (CTE) of the CMC pipe in
circumferential direction (ratio of wall thickness 1:1, no gap)
steel only
CMC 1,6 x 10-6 K-1
CMC 7,4 x 10-6 K-1
CMC reinforcements with higher CTEs reduce the stress
level of the two coaxial pipes due to the smaller mismatch
of the thermal expansion
FE Simulations – Hoop Stress: Influence of CTE
Ho
op
str
es
s
All results are normed to the value of
the inner hoop stress of the steel pipe
1 2
3 4
steel CMC
1 2 34
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• Increase of lifetime by more than factor 4
• Local damage of the CMC jacket after 3655 h
• Non-catastrophic damage behavior due to local
creep failure of the steel pipe
• Proof of concept successful
steel pipe
local creep deformation
of steel pipe
cracked CMC pipe
CMC pipe
No separation of the CMC jacket of
the steel pipe
steel pipe
Hyb
rid
ce
ram
ic-m
eta
l p
ipe
Proof of Concept
Bru
ssels
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CMC load bearing
structure
SiSiC-tubes
Process gas (20 bar)
Exhaust gas (1 bar)
Separation of functions:
• CMC load bearing structure for high thermomechanical strength and reliability
• Monolithic ceramic tubes for gas tightness and high corrosion stability
• Interphase of high TC (BN, AlN) compensates manufacture tolerances
Full-Ceramic Heat Exchanger
Europ. Patent EP 0 996 848
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Summary
• The different CTEs of metals and ceramics require strain-compatible
attachments
• Joining of similar materials (in-situ-joining) results in lowest thermally induced
stresses
• Ceramic Matrix Composites allow the design of highly and permanently tensile
loaded structures
• The high anisotropy and the very low CTEs of CMCs still remain challenges in
designing with ceramics
• Change of Design in Ceramics: “From the compression-loaded arch to the
tension-loaded beam“