towards sustainable fuels and clean combustion concepts: progress in combustion...
TRANSCRIPT
Towards sustainable fuels and clean combustion
concepts: Progress in Combustion Control and Advanced
Optical Diagnostics
Prof. Dr.-Ing. Michael Wensing
Lehrstuhl für Technische Thermodynamik LTT
Friedrich-Alexander Universität Erlangen-Nürnberg FAU
FAU is one of the ten largest universities in Germany
and one of the leading universities in Europe.
FAU is ranked as the second most innovative university
in Germany by absolute numbers of patents and
publications on innovative technologies,
per professor it is number one.
Of the 39.780 students (winter semester 2017/2018)
at FAU, 19,663 are female and 4,890 are international students.
FAU currently offers 265 degree programmes, including 80 Bachelor’s degree
programmes, 94 Master’s degree programmes and 91 Staatsexamen (state
examinations) degree programmes (in subjects such as teaching, law and
medicine).
In 2016, 7,274 students graduated from FAU, in 2016 766 completed their doctoral
degrees and 51 post-doctoral students completed their habilitation. FAU has a total
of 579 professors. With a total of 177,6 million euros (2016), FAU has one of the
highest volumes of third-party funding of all the universities in Germany.
FAU Key figures at a glance:
275 Years of FAU
Knowledge in Motion
23.08.2018 3
• In Germany now we have 35% of wind and solar electricity
(cumulative)
• CO2 reduction limited due to very limited flexibility
• Volatility and limitations of transfer (between times, areas
and intersectional) have been underestimated an
increasingly come in force
• E-mobility is only a part of a solution
• Thermal energy sector is very important
• Pressure of fossil and nuclear energy carriers
• The use of CO2 as feedstock rather than as waste is
demonstrated in nature in large scales
• Energy can be stored/handled in two ways: free electrons or
chemical bonds
Energy situation in Germany
Energy density in comparison
0
2
4
6
8
10
12
14
12,2
0,08 0,003
10,3
0,07 0,003
Potentials: Energy density of different storage possibilities
• Power of a single filling station at 35l/min: 21,6 MW
• One ship can supply 10 power stations
• The wind and solar power installed in Germay equivals to the Peak-
consumption
Energy density kWh/l
Energy density kWh/kg
Chemical
Storage (Diesel)Elektr.
Battery (BMW i3)
Hydro
Power (1000m)
Task: Sustainable Fuels, low emission, competitive price
23.08.2018 5
Carnot & Pischinger
Motorische
Brennverfahren und
Kraftstoffe
SI engines CI engines
source:
Boschsource:
Bosch
1
2
4
3
p
v
T=const
T=const
s=
const
s=co
nst
Q0
Q
T
s
Q
Q0
4
3TH
T0
23.08.2018 6
Topics
New fuels in mixing controlled combustion concepts
Enhanced combustion control by reduced chemical
complexity
New Ignition Concepts for homogeneous lean combustion
concepts
Enabler for efficiency improvement in a low emission
combustion concept
Hydrogen and LOHC
Possibilities and challenges of an carbon free energy
carrier
23.08.2018 7
Mixing controlled combustion
Atomization investigated by X-Rays
Region of interest
Cooperation with Dr. Jin Wang,
Argonne National Labs, USA
Cooperation with Dr. Edouard
Berrocal, Lund Univ. Sweden
0,5
mm
1,0 mm
8
Primary Breakup of Diesel SprayspFuel = 1000 bar / pGas = 1 bar
X-Ray High Speed Investigation Diesel
300 μm 300 μm
Masse density*velocity spray strukture
* © Density Evaluations Gröger, Dinkelacker, ITV Hannover
23.08.2018 9
Fundamentals of Disel sprays
Momentum balance, Wakuri (1960), Siebers (1996 – 1999)
entrained ambient gas ρa, Ta, pa
θ
Fuel
ρf, Tf,
pa mix
ture
Assumptions:
• Rectangular velocity profile
• Exclusively radial air movement
outside the spray (Zhu 2013: LIF/PIV)
• Stationary injection conditions, i.e.
constant nozzle exit velocity and cone
angle θ
• No-slip-condition between fuel and
ambient gas
• Constant density of ambient gas
mf
ma=
2
1 + 16 x2 − 1
mf = ρf0 ∙ A0 ∙ u0
ma = ρa ∙ A x ∙ u x
mf ∙ u0 = mf + ma ∙ u x
x =ρaρf
∙x
Ca ∙ d∙ tan
θ
2
20 mm
23.08.2018 10
MotivationHow much air is entrained during the mixing process?
0,0
0,5
1,0
1,5
2,0
0 200 400 600 800
mass r
ati
o f
uel/air
t avSoI / µs
0
20
40
60
80
100
0
500
1000
1500
2000
2500
0 200 400 600 800
VF
uel/ m
m³
VS
pra
y/ m
m³
t avSoI / µs
spray plume
fuel
How does it look like locally?
using Raman-spectroscopy
Investigated with 3-hole research injector from Continental
d = 115 μm used fuels: GtL-Diesel
mFuel = 12.3 mg n-Decane
θ = 22°, cA ≈ 0.95 Ethanol
23.08.2018 11
Geometrical relationship between spray plume and measuring
heightsExemplary spectrum above the nozzle tip
H20
H10
H7
H5
H2
a < bx
y025
Laser
beam
locations
0
50
100
150
200
250
2200 2400 2600 2800 3000 3200 3400 3600 3800
Inte
nsity
[counts
]
Raman shift [cm-1]
N2
CH
OHlo
cation
x
wavelength
IR = signal intensity n = number density
kA = setup influences 𝜎R = scattering cross section
𝐼𝑅 ~ 𝑘𝐴∙𝜎𝑅∙𝑛
45°
ICH =
i=2700
3100
IR i
23.08.2018 12
Molar and mass fraction for different fuelspa = 6 MPa, Ta = 923 K, pf = 120 MPa, Tf = 363 K, tavSoI = 700 μs
0
0,05
0,1
0,15
0,2
0,25
0,3
0,35
0,4
0,45
0,5
0 1 2 3 4 5
nf/
na
location / mm
ethanol
decane
GtL-diesel
0
0,1
0,2
0,3
0,4
0,5
0,6
0,7
0,8
0 1 2 3 4 5
mf/ m
a
location / mm
ethanol
decane
GtL-diesel
Height: 5 mm
23.08.2018 13
Air-entrainmentClassification within limits of possible air-entrainment situations
0
0,5
1
1,5
2
2,5
3
0 10 20 30
mf/m
a/ -
x / mm
Schlieren penetration
Mass ratio based on measured spray front penetration:
Derived spray front velocities from Schlieren
measurements
Following momentum conservation
Stationary spray: tavSoI = 700 μs
mf
ma(x)=
1u0u(x)
− 1
0
0,5
1
1,5
2
2,5
3
0 10 20 30
mf/m
a/ -
x / mm
Schlieren penetration
momentum conservation(ideal)
Ideal mass ratio based on total momentum conservation
mf
ma(x)=
2
1 + 16 ⋅ρaρf⋅xd
2⋅ tan2
θ2
− 1
Measured ratios are fitted with Gaussian distribution
Peak value defines spray axis
Using hyperbola fit function
0
0,5
1
1,5
2
2,5
3
0 10 20 30
mf/m
a/ -
x / mm
Schlieren penetration
momentum conservation(ideal)
Raman Fit
Raman measurements
23.08.2018 14
Transformation from 1D measurements to
2D image
0.5
0.4
0.3
0.2
0.1
0.0
mf
ma
mm
mm
23.08.2018 15
Results
New fuels in mixing controlled combustion concepts
Enhanced combustion control by reduced chemical
complexity
• Diesel sprays mainly consist of air
• Droplets are not important in Diesel Sprays
• Mass distribution is governed by momentum balance
• Molar distribution and air fuel ratios depend on molar
masses
=> Mixture formation (parameters of the injection system)
and combustion (chemical properties of the fuel) can
be handled separately
23.08.2018 16
Topics
New fuels in mixing controlled combustion concepts
Enhanced combustion control by reduced chemical
complexity
New Ignition Concepts for homogeneous lean combustion
concepts
Enabler for efficiency improvement in a low emission
combustion concept
Hydrogen and LOHC
Possibilities and challenges of an carbon free energy
carrier
23.08.2018 17
SI Combustion concepts, Eta (Epsilon, Kappa)
Efficiency of SI engines limited
• Knocking tendency
• Ignitability of diluted or lean mixtures
• Stoichiometric combustion concept, 3-way-
Catalyst
• NOx Emissions 1.05>λ>1.6
Higher ignition energy needed for λ>1.6 !
Pre-Chamber Ignition
source:
Bosch
23.08.2018 18
SI Combustion concepts
2. New ignition concepts
Main differences and tasks
• Higher power density and speed
• Small space available
• Only liquid fuel available
Large gas engine Race car
19Pre-Chamber Ignition System – Moritz Schumacher
Results
λ-Variation
Low load operating point with
4.5 bar IMEP - 1500 rpm
Two Pre-Chamber designs with
small / large volume and transfer ports
• Ability to ignite mixture up to λ=2
• Lean misfire limit increased to λ≈1.8
• Losses in efficiency due to large PC
• Reduced compression ratio
• Higher heat losses
• Higher fuel consumption of PC
• Engine out NOx emissions at lean limit
below 20 ppm
• Further reduced burn duration
-0,5
0,0
0,5
1,0
1,5
2,0
0
5
10
15
20
25
-360 -300 -240 -180 -120 -60 0 60 120 180 240 300 360
PC
Fue
l pre
ssu
re /
bar
Cyl
ind
er
pre
ssu
re /
bar
Crank Angle /°
PCPr2
PCoPr2
CylPr2
PCValve2
PCFuelPr
20Pre-Chamber Ignition System – Moritz Schumacher
Results
Variation of EGRLow load operating point with 4.5 bar IMEP -
1500 rpm
• Variation of inlet phase (EGR rate) @ λ = 1
• Tubmble flaps open (low tumble)
• With / without additional air scavenging of PC
• EGR tolerance much higher with air scavenging
Gasoline
vapourAir
21Pre-Chamber Ignition System – Moritz Schumacher
Results – Volume Ignition / Stratification
Stratified Combustion
• Injector position and targeting NOT
optimized for stratified injection
• Typical side injector position and targeting
• EOI near ignition timing at 18°BTDC
• PC fuel only from PC fuelling system,
no fuel from combustion chamber in PC
• Stable stratified combustion
Pre-chamber jets ignite stratified charge
“Volume Ignition”
22Pre-Chamber Ignition System – Moritz Schumacher
Results
Cylinder / Pre-Chamber Pressure Analysis
• Overpressure in Pre-chamber
increased to 7.5 bar compared to
1.8 bar with old design
• Improved measurement
technique with real-time
evaluation of PC combustion
• Overpressure
• Timing and Duration
• Stability
New Pre-chamber design with
larger volume at λ=1.6
4.5 bar IMEP and 1500 rpm
Cylinder pressure
PC pressure
Overpressure in PC
SoC
Pmax, Pmax Cov
23.08.2018 23
Results
New Ignition Concepts for homogeneous lean combustion
concepts
Enabler for efficiency improvement in a low emission
combustion concept
• Homogeneous lean combustion with <20ppm NOx is
possible
• Active pre-chamber ignition enables high efficiency
diluted charge combstion concepts
• Ultra Lean Combustion
• High EGR Stochiometric Combustion
=> High efficiency potenzial for SI combustion
23.08.2018 24
Inhalt
New fuels in mixing controlled combustion concepts
recent results using advanced diagnotics like High Speed
(HS) X-Ray imaging, HS-Schlieren, HS-Mie and Raman
Spectroscopy
New Ignition Concepts for homogeneous lean combustion
concepts:
efficiency potentials for SI engines
Hydrogen and LOHC
possibilities and challenges of an carbon free energy
carrier
23.08.2018 25
Hydrogen
Example MAN 2876
• Available for different fuels
• 6-cylinder inline engine
• 12,8 l displacement
Property Unit Diesel CH4 H2 (2G)
Power kW 330 210 130
BMEP bar 20,6 13,1 8,1
Lambda 1,6 3
Compression 15,5 13,5 11
Eff. Efficiency % 41,8 39 39,3
Power density
of fuelMJ/l 38,7 0,0317 0,0108 Source: MAN
• Hydrogen is a very special fuel for internal combustion engines
• Low density and high wall heat losses during combustion
Boosted lean operation with low pressure direct injection
Good power density, high efficiency and low emissions
23.08.2018 26
• LOHCs store hydrogen
from fluctuating renewable
energies
• Storage of LOHCs
possible like diesel fuel
• Release of hydrogen by
means of catalyst and
heat
Hydrogen
23.08.2018 27
Inhalt
Hydrogen and LOHC
possibilities and challenges of an carbon free energy
carrier
Energy
Therm.
Engines
Fuel Cells
Drop-In
Strategies
Chemical
Nox-Reduction
Improve
Waste-to-
Diesel
HQ-Fuels
Heavy Oils
Biofuels
23.08.2018 28
Summary
Thanks for your
Attention!
The Internal Combustion Engines Group
Gasoline
Sprays
Diesel
Sprays Combustion
Concepts
Thanks for your
Attention!
23.08.2018 31
Experimental setupAssembly on spray chamber
beam forming optics
laser @ 532nm
spectograph with
EMCCD camera
Raman
signal
spray
plumes
beam waist
ØBW ~ 200µm
Galilean telescope
ØLB = 50mm
Laser beam
ØLB = 12mm
heig
ht
23.08.2018 32
CalibrationHow to calibrate on a permanently scavenged chamber?
Fuel
N2 0
0,2
0,4
0,6
0,8
1
0 1 2 3 4 5
I f/I
a/ -
location inside the beam waist / mm
v̇a = 0.173 m³/h v̇f = 5.39 ml/minv̇a = 0.172 m³/h v̇f = 5.39 ml/minv̇a = 0.172 m³/h v̇f = 5.39 ml/min
R² = 0,9995
0,0
1,0
2,0
3,0
4,0
5,0
6,0
0,00 0,02 0,04 0,06 0,08
I f/I
a/ -
nf/na / -
IfuelIambient
nfuelnambient
𝑘 =
𝑛𝑓𝑢𝑒𝑙𝑛𝑎𝑚𝑏𝑖𝑒𝑛𝑡
𝐼𝑓𝑢𝑒𝑙𝐼𝑎𝑚𝑏𝑖𝑒𝑛𝑡
⇒𝑛𝑓𝑢𝑒𝑙
𝑛𝑎𝑚𝑏𝑖𝑒𝑛𝑡=
𝐼𝑓𝑢𝑒𝑙
𝐼𝑎𝑚𝑏𝑖𝑒𝑛𝑡 ⋅ 𝑘
23.08.2018 33
Molar and mass fraction within the spray
plumepa = 6 MPa, Ta = 923 K, pf = 120 MPa, Tf = 363 K, tavSoI = 700 μs
fuel: ethanol
0
0,2
0,4
0,6
0,8
1
1,2
1,4
0 1 2 3 4 5
nf/
na
location / mm
H = 2mm
H = 5mm
H = 7mm
H = 10mm
H = 20mm
0
0,2
0,4
0,6
0,8
1
1,2
1,4
1,6
1,8
2
0 1 2 3 4 5
mf/ m
a
location / mm
H = 2mm
H = 5mm
H = 7mm
H = 10mm
H = 20mm
23.08.2018 34
Wavele
ng
th[n
m]
location
N2
CH
-0,1
0,0
0,1
0,2
0,3
0,4
800 1200 1600 2000 2400 2800 3200
no
rmalisie
rte I
nte
nsit
ät
[ -
]
Raman-Shift ΔωR [cm-1]
normalisiertesSpektrumFit CH-Peak
Fit N2-Peak
Mixing controlled Combustion
3. Raman Detail, Bio-EFuels