Firenze, 6 Novembre 2018 Combustori di Micro Turbine a Gas ... · Combustori di Micro Turbine a Gas...
Transcript of Firenze, 6 Novembre 2018 Combustori di Micro Turbine a Gas ... · Combustori di Micro Turbine a Gas...
-
Combustori di Micro Turbine a Gas Alimentati a Syngas o Miscele
Gas Naturale – Idrogeno
Maria Cristina CAMERETTI
Raffaele TUCCILLO
Roberta DE ROBBIO
Dipartimento di Ingegneria Industriale
Università di Napoli Federico II, Italy
GIORNATA DI STUDIO SUI COMBUSTORI DI TURBINA A GAS
Firenze, 6 Novembre 2018
Fabrizio REALE
Fabio CHIARIELLO
Istituto Motori del CNR,Napoli, Italy
1
-
RESEARCH ACTIVITIES IN GAS TURBINE COMBUSTION BY CFD MODELS
The object of the studies are two micro gas turbine withdifferent combustor:
1. A 100kW MGT with tubular LPP combustor
2. A 30 kW MGT with annular reverse flow combustor
3. A 100 kW MGT with LP
reverse flow combustor
2
-
MGT features MICRO-GT SPECIFICATIONS Mech. Arrangement Single Shaft Pressure Ratio 3.9 Turbine Inlet Temp. 1223 K Combustor Inlet Temp. 905 K Overall fuel/air Eqv. Ratio 0.125 Rated Mech. Output/ Speed 110 kW / 64000 rpm Compressor 1 Radial Flow Compressor Turbines 1 Radial Flow Turbine
1. A 100kW MGT with tubular LPP combustor
3
-
Micro gas turbine (MGT) combustorfuelling with gaseous fuels from biomasstreatment or solid waste pyrolysis.
The objective is to optimize the combustor behaviour
under the point of view of combustion efficiency and
pollutant control
Cycle Analysis and CFD simulationhighlight the possible benefits and the
major problems
The combustion development is analyzed by a combined
approach based on the partially stirred reactorhypothesis and on the flamelet concept within aCFD simulation
COMBUSTION ANALYSIS IN A MICRO-GAS TURBINE
SUPPLIED WITH GASEOUS BIO-FUELS
4
-
Table 1. Natural gas and biogas properties
Fuel Compos.(%, molar)
NAT. GAS (NG)
BIOMO BIOMABIOM(AD)
SW
CH4 92.00 18.00 9.00 65.00 7.00C2H6 3.70 2.00 - - - - 7.00
C3H8 1.00 2.00 - - - - 7.00
C4H10 0.25 2.00 - - - - - -
N2 2.90 8.00 56.00 - - - -
H2 - - 25.00 9.00 - - 18.00CO - - 33.00 12.00 -- 61.00CO2 0.15 10.00 20.00 35.00 - -
H2O - - - - - - - - - -
Mol. Mass, g/mol 17.34 21.92 28.51 25.83 23.76
LHV, kJ/kg 47182 19198 2798 20183 21697
fst 0.0620 0.1680 1.257 0.145 0.1530
Tof, K 2220 2231 1571 2126 2300
f
j
0.0082
0.132
0.0214
0.127
0.191
0.151
0.0202
0.139
0.0177
0.115 5
-
THE CFD SIMULATIONS WITH THE
STEADY FLAMELET APPROACH
9
-
Standard and Modified pilot injector locations streamline pattern
(Attempt to approach the MILD Combustion regime)
Standard Pilot
Location
Modified Pilot
Location
10
-
CFD analysis:
Three chemical reaction set
1) A set of single – step oxidation of the several speciesconstituting the fuel (only the CH4 oxidation proceedsthrough two steps, i.e. partial and CO oxidation)
6,1215,0
104
809
222104
65,1
2
1,0
83
809
2283
65,1
2
1,0
62
809
22262
25,0
2
18
12
22
8,0
2
7,0
4
811
224
10256,1exp10161,4
542
13)5
10256,1exp1062,5
432
7)4
10256,1exp10186,6
322
7)3
102exp10239,2
2
1)2
102exp10012,5
22
3)1
OHCRT
R
OHCOOHC
OHCRT
R
OHCOOHC
OHCRT
R
OHCOOHC
OCORT
R
COOCO
OCHRT
R
OHCOOCH
f
f
f
f
f
11
-
T
T
T
T
PPP
T
PPPP
T
P
P
T
P
PPPP
T
PPP
eTONR
NOON
eONR
NOON
eTOOHNR
NOON
eCOOR
NOON
eCOOR
NOON
eCOR
OCOCO
e
OOHCOR
COOCO
eCOOCHR
OHCOOCH
68899
5.05.0
22967.14
8
22
52861
22317.10
7
22
69158
7.025.02
5.022
592.146
22
31.3348.6492504880.07911.24613.2
2
)log(7822.48327.29
5
22
6.126467480006.08888.00344.01805.1
20376.0122.14
4
22
31.3348.64925
207163.08144.15
3
22
1.7522398
0127.0891.02
0909.00912.02
0109.0359.11091.0338.142
22
4.269219321987.001426.0
201148.03.1
4004628.0354.13
1
224
10
2)8
10
2)7
10
2)6
10
2)5
10
2)4
10
21)3
10
21)2
10
223)1
the 8-step scheme (Novosselov and Malte,2007) accounts for both thermal and flame-prompt NO formation
the kinetic scheme is pressure-sensitive
Suitable for variable load operations
CFD analysis:
2) An eight-step scheme
The reaction mechanism is based on the
Finite Rate – Eddy Dissipation model
12
-
3) The GRIMECH 3.0 scheme (53 species, 325 reactions)
The steady, non-adiabatic flamelet concept allows solution of such
a complex system of non-linear equations thanks to the
preliminary set-up of flamelet tables and, consequently, of PDF
(probability density function) tables.
This algorithm replaces in an effective way the attempt to the
simultaneous solution of hundreds of kinetic equations with a
single additional equation of the scalar variable “mean mixture
fraction”
ffvf
t t
t
13
-
SENSITIVITY ANALYSIS ON COMBUSTIONAND TURBULENCE MODEL.
Table 3. Volume averaged and outlet properties from CFD based
simulations: comparison of different schemes (natural gas fuelling)
OXIDATION SCHEME
Volume Outlet
O2
%,
mol
TmaxK K
[NO]
p.p.m.
[CO]
p.p.m
.
[UHC]
%
1-step 18.05 2700 1180 67 117 0.407
8-step 17.37 2348 1228 63 515 0.043
Flamelet (k-e) 18.17 2308 1147 72 2.8 3.22
Flamelet (k-w) 17.72 2091 1207 99 1.4 1.89
Flamelet (RS) 17.86 2287 1064 71 2.1 3.17
14
-
Results:Temperature distributions for
different Reaction schemes adopted
Temperature, K
1-Step Oxidation
8-Step Oxidation
Flamelet
flamelet approach returns much smoother temperature profiles
than in the reduced kinetics cases
15
-
Results: NO profiles for different oxidation
schemes
16
-
Results:. Axial developments of flame speed
17
-
The effect of the increased fuel pilot rate on the progress variable and the
turbulent flame speed
To improve the overall reaction speed the
amount of fuel injected through the pilot
line has been increased
18
-
Temperature distributions
for different pilot injections
BIOMO_1PIL
BIOMO_3PIL
BIOMO_2PIL
SW_1PIL
SW_3PIL
SW_3PIL – Modified Pilot Location
19
-
• The temperature peaks with the BIOMO and SWfuels are higher than in the methane fuelling case,
because of the combined effect of their hydrogen
contents with the one of the increased pilot flow rate
Volume averaged and outlet properties from CFD based simulations: comparison of different fuels
OXIDATIONSCHEME
Volume Outlet
O2
%, mol
TmaxK K
[NO]p.p.m.
[CO]p.p.m.
[UHC]%
Methane 18.17 2308 1147 72 2.8 3.22
BIOMO_1PIL 18.15 2084 1146 88 3327 1.81
BIOMO_3PIL 17.78 2513 1165 94 2832 1.54
Biogas_3PIL 17.25 2342 1200 68 0.221 3.14SW_3PIL 17.76 2537 1198 126 3301 0.382SW_PIL (mod.) 17.97 2486 1142 62 5444 0.624
20
-
Profiles of turbulent flame speed and nitric monoxide for different pilot
locations (SW_3PIL case)
21
-
LIQUID FUEL
SPRAY ANALYSIS
AIRBLAST ATOMIZER
22
-
LPP Combustor
NOx Emissions
Abatement
• Homogeneous Mixture• Low Flame Temperature• Hot Spots Absence
Fuel % to pilot 10%
Pilot line equiv. Ratio 1
Main line equiv. Ratio 0.5
Overall equiv. Ratio 0.1546
23
-
LPP Combustor
60° Sector
25
-
AIRBLAST MODEL
Ligament constant [m] 0.5
Sheet breakup empirical constant 12
Fuel flow rate [kg/s]0.0013 (kerosene)
0.0020 (ethanol)
Spray half angle θ Variable
Maximum relative velocity [m/s] Variable
Fuel Temperature [K] 300
Injector Inner Diameter d [µm] 300
Injector Outer Diameter D [µm] 409.8
Airblast Atomizer
The atomization is due to the high speed inner air flow
• Insensitivity of the outlet temperature traverse to changes in fuel flow.• High pressure fuel pumps are not needed.• Component parts are protected from overheating by the air flowing over them.
26
-
TURBULENCE:
MULTIPHASE:
SPRAY EVOLUTION:
COMBUSTION:
Realizable k-ε model
Lagrangian Discrete Phase Model
TAB model
Finite Rate – Eddy Dissipation
Models
STOCHASTIC
COLLISION:O’Rourke Algorithm
27
-
Fuels
FUELKerosene Bio-
Ethanol
LHV, kJ/kg 43124 27500
fst 0.0685 0.0957
Dynamic viscosity, kg/(m s) 0.0024 0.0012
Density, kg/m3 780 794
Surface Tension, N/m 0.0263 0.0223
Vaporiz. Temp , K 341 271
Normal Boiling Point, K 477 351
Volumetric coefficient of
expansion, 1/K0.00099 0.00112
𝑊𝑒 =𝜌𝑔𝑈𝑅
2𝐷
𝜎
𝜙 =𝑓
𝑓𝑠𝑡
Higher fuel consumption
for Ethanol
Responsible of a faster
vaporization
28
-
1. Cold Flow, Non-Evaporating Conditions:
Kerosene Results
170° 150°
90° 60°
Droplet
Diameter
[mm]
120°
30
-
1. Cold Flow, Non-Evaporating Conditions:
Comparison
𝑊𝑒 =𝜌𝑔𝑈𝑅
2𝐷
𝜎
FUEL Kerosene Ethanol
σ, N/m 0.0263 0.0223
31
-
2. Hot Flow, Evaporating Conditions:
Results Kerosene
32
-
2. Hot Flow, Evaporating Conditions:
Comparison
170°
170°
34
-
3. Burning Conditions
60°
60°
37
-
SPRAY ANGLE = 60°
Kerosene
Ethanol
3. Burning Conditions
41
-
3. Burning ConditionsFuel Kerosene Ethanol
CO [ppm] 1683 171 1138 456
42
-
2. 30 kW MGT
Annular Combustor
The work is based on a study of the potential of a micro gas
turbine (MGT) combustor when operated under
unconventional conditions, both in terms of variation in the
fuel supplied and concerning the part-load or off-design
operation
1. Description of the combustor of C30 micro gas turbine
2. A CFD analysis of the reacting flow through the MGT combustor checks thecombustion effectiveness under challenging variations of the boundary condition
3. Comparison of the combustor response at base-rating and part load
4. Combined use of natural gas and hydrogen in the micro gas turbine
5. Splitting the fuel delivery into two distinct streams, the first one (with only Hydrogen)
coming from the pilot injection, the second one flowing main injector line with air and
NG premixing
43
-
• DESCRIPTION OF THE COMBUSTOR
Dimension [mm]
External diameter 242
Minimum internal
diameter51
Outlet diameter 139
Internal liner length 249
External liner length 233
Total length 280
DESCRIPTION OF THE COMBUSTOR
44
-
Domain Fine Coarse
Pilot 1350 800
Premix 33000 24000
Liner 130000 55000
Core 240000 44000
COMPUTATIONAL MESH
45
-
• The CFD analysis was performed with the ANSYS-FLUENT solver of the reacting flow
• for each case the related boundary conditions were provided by a thermal cycle analysis
30 kW MGT base-rating data
Shaft Speed 96000 rpmFiring Temperature 1173 KPressure Ratio 3.5Fuel flow rate [kg/s] 0.0026
Fuel Energy rate [kW] 115.4
Fuel Heat rate [kJ/kWh] 14208
Recovered Heat from exhausts [kW] 51.33
Fuel Energy Utilization factor 0.695
Overall Electric efficiency 26.05%
CO2 [kg/h] (kg/kWh) 24.37
(0.812)
46
-
CHEMICAL KINETICS
• Methane three-step oxidation mechanism (by Novosselov andMalte ) completed by a 5-equation set for the thermal and prompt
NO formation
𝑪𝑯𝟒 +𝟑
𝟐𝑶𝟐 → 𝑪𝑶+ 𝟐𝑯𝟐𝑶
𝑅1 = 1013.354−0.004628𝑃 𝐶𝐻4
1.3−0.01148𝑃 𝑂20.01426 𝐶𝑂 0.1987
𝑒𝑥𝑝 − 182342648 + 2.2398 × 106𝑃 /𝑅𝑇
𝑪𝑶 +𝟏
𝟐𝑶𝟐 → 𝑪𝑶𝟐
𝑅2= 1014.338+0.1091𝑃 𝐶𝑂 1.359−0.0109𝑃 𝐻2𝑂
0.0912+0.0909𝑃 𝑂20.891+0.0127𝑃
𝑒𝑥𝑝 − 186216972 + 6.2438 × 105𝑃 /𝑅𝑇
𝑪𝑶𝟐 → 𝑪𝑶+𝟏
𝟐𝑶𝟐
𝑅3= 1015.8144−0.07163𝑃 𝐶𝑂2 𝑒𝑥𝑝 − 5.3979 × 10
8 − 2.7795 × 106𝑃 /𝑅𝑇
𝑵𝟐 +𝑶𝟐 → 𝟐𝑵𝑶𝑅4 = 10
14.122+0.0376𝑃 𝐶𝑂 0.8888−0.0006𝑃 𝑂21.1805+0.0344𝑃
𝑒𝑥𝑝 − 388662872 + 1.0526 × 106𝑃 /𝑅𝑇
𝑵𝟐 +𝑶𝟐 → 𝟐𝑵𝑶
𝑅5 = 1029.8327−4.7822 log10 𝑃 𝐶𝑂 2.7911−0.04880𝑃 𝑂2
2.4613
𝑒𝑥𝑝 − 509357210 + 5.8589 × 106𝑃 /𝑅𝑇
𝑵𝟐 +𝑶𝟐 → 𝟐𝑵𝑶
𝑅6 = 1014.592 𝑁2 𝐻2𝑂
0.5 𝑂20.25𝑇−0.7𝑒𝑥𝑝(−
574979612
𝑅𝑇)
𝑵𝟐 +𝑶𝟐 → 𝟐𝑵𝑶
𝑅7 = 1010.317 𝑁2 𝑂2 𝑒𝑥𝑝(−
439486354
𝑅𝑇)
𝑵𝟐 +𝑶𝟐 → 𝟐𝑵𝑶
𝑅8 = 1014.967 𝑁2 𝑂2
0.5𝑇−0.5𝑒𝑥𝑝(−572826286
𝑅𝑇)
47
-
• OXIDATION MECHANISM OF THE OTHER HYDROCARBONS INNATURAL GAS (NG).
𝑪𝟐𝑯𝟔 +𝟕
𝟐𝑶𝟐 → 𝟐𝑪𝑶𝟐 + 𝟑𝑯𝟐𝑶
𝑅9 = 6.186 × 109 𝐶2𝐻6
0.1 𝑂21.65𝑒𝑥𝑝(−
1.256 × 108
𝑅𝑇)
𝑪𝟑𝑯𝟖 +𝟕
𝟐𝑶𝟐 → 𝟑𝑪𝑶𝟐 + 𝟒𝑯𝟐𝑶
𝑅10 = 5.62 × 109 𝐶3𝐻8
0.1 𝑂21.65𝑒𝑥 𝑝 −
1.256 × 108
𝑅𝑇
𝑪𝟒𝑯𝟏𝟎 +𝟏𝟑
𝟐𝑶𝟐 → 𝟒𝑪𝑶𝟐 + 𝟓𝑯𝟐𝑶
𝑅11 = 4.161 × 109 𝐶4𝐻10
0.15 𝑂21.6𝑒𝑥𝑝(−
1.256 × 108
𝑅𝑇)
48
-
ALL TEST CASES INVOLVING HYDROGEN CONTENTS
HAVE BEEN SIMULATED WITH THE JACHIMOWSKI
REDUCED SCHEME
𝑯+𝑶𝑯+𝑴 = 𝑯𝟐𝑶+𝑴𝑅1 = 2.21 × 10
16 𝐻 𝑂𝐻 𝑇−2
𝑯+𝑯+𝑴 = 𝑯𝟐 +𝑴𝑅2 = 7.3 × 10
11 𝐻 𝐻 𝑇−1
𝑯𝟐 +𝑶𝟐 = 𝑶𝑯+𝑶𝑯
𝑅3 = 1.7 × 1010 𝐻2 𝑂2 𝑒𝑥𝑝(−
2.0083 × 108
𝑅𝑇)
𝑯 + 𝑶𝟐 = 𝑶𝑯+𝑶
𝑅4 = 1.2 × 1014 𝐻 𝑂2 𝑇
−0.91𝑒𝑥𝑝(−6.9086 × 107
𝑅𝑇)
𝑶𝑯+ 𝑯𝟐 = 𝑯𝟐𝑶+𝑯
𝑅5 = 2.2 × 1010 𝑂𝐻 𝐻2 𝑒𝑥𝑝(−
2.1548 × 107
𝑅𝑇)
𝑶+𝑯𝟐 = 𝑶𝑯+𝑯
𝑅6 = 50.6 𝑂 𝐻2 𝑇2.67𝑒𝑥 𝑝 −
2.6317×107
𝑅𝑇(3)
𝑶𝑯+𝑶𝑯 = 𝑯𝟐𝑶+ 𝑶
𝑅7 = 6.3 × 109 𝑂𝐻 𝑂𝐻 𝑒𝑥𝑝(−
4560560
𝑅𝑇)
𝑵 + 𝑵 +𝑴 = 𝑵𝟐 +𝑴𝑅8 = 2.8 × 10
11 𝑁 𝑁 𝑇−0.8
𝑶+ 𝑶+𝑴 = 𝑶𝟐 +𝑴𝑅9 = 1.1 × 10
11 𝑂 𝑂 𝑇−1
𝑵+𝑶𝟐 = 𝑵𝑶+𝑶
𝑅10 = 6400000 × 𝑁 𝑂2 𝑇1𝑒𝑥𝑝(−
2.6359 × 107
𝑅𝑇)
𝑵 + 𝑵𝑶 = 𝑵𝟐 + 𝑶𝑅11 = 1.6 × 10
10 𝑁 𝑁𝑂
𝑵+𝑶𝑯 = 𝑵𝑶+𝑯𝑅12 = 6.3 × 10
8 𝑁 𝑂𝐻 𝑇0.5 49
-
• combustion modelsand turbulence-chemistry interaction
1) FINITE RATE – EDDY DISSIPATION MODEL (FRED):
reaction rates are compared with those evaluated by the turbulent
mixing of the reactants, the latter estimated by a k-w model
2) COMBUSTION MODEL BASED ON THE EDDY DISSIPATION
CONCEPT (EDC)
• More reliability in the treatment of multiple reactions in hydrogen turbulent combustion
50
-
PRELIMINARY CFD ASSESSMENT
COMPARISON BETWEEN THE TWO MODELS FREDand EDC:
Temperature distributions (K)
FRED Model – Fine Grid
EDC Model – Fine Grid
EDC Model – Coarse Grid
mesh sensitivity analysis
51
-
Injector plane
Meridional plane
Cross plane
STREAMLINES
53
-
Turbulent Intensity
Specific Dissipation Rate
54
-
• EDC model
COMPUTATIONAL TEST-CASES
Boundary condition data for the combustion simulation
(NG Operation)
Base Rating 70% Load
Combustor Inlet Temp. (K) 870 883
Combustor Outlet Pressure (bar) 3.20 2.62
Fuel mass flow rate (kg/s)0.00292
(from premixed line)0.00183
(from pilot line)
Oxidant mass flow rate (kg/s) 0.306 0.270
Overall equivalence ratio 0.143 0.102
55
-
• Testing the Pilot Line Response
COMPUTATIONAL TEST-CASES
Base – Rating
Rate of
reaction,
kg/(m3s)
70% Load
56
-
• Testing the Pilot Line Response• at full load the ignition begins near the injector outlet due to
the fuel/air premixing;
• at part load the unmixed fuel reaches the maximum value of the reaction rate far from the injector outlet
• The new proposal is the simultaneous employment of the premixer and pilot line in the case of combined use of natural
gas and hydrogen.
• The purpose is overcoming typical early ignition and flashback limits when firing hydrogen
COMPUTATIONAL TEST-CASES
57
-
Test cases with combined fuelling of Natural Gas and
Hydrogen
case#1 Base – Rating, Natural Gas from premixer
case#290% NG from premixer – 10% H2 from pilot
(Nitric Oxides from Novosellov and Malte scheme)
case#390% NG from premixer – 10% H2 from pilot
(Nitric Oxides from Jachimowski scheme)
case#475% NG from premixer – 25% H2 from pilot
(Nitric Oxides from Jachimowski scheme)
case#575% NG– 25% H2 mixture from premixer
(Nitric Oxides from Jachimowski scheme)
COMPUTATIONAL TEST-CASES
58
-
COMPUTATIONAL TEST-CASES
Volume averaged and outlet properties from CFD
based simulations
CASE
Volume Outlet
TmaxK
ToutK
[NO]
p.p.m.
[CO]
p.p.m.
Burned
[CH4] %
Burned
[H2] %
# 1 2567 1206 5.07 462 99.86 --
#2 2274 1159 3.82 841 99.60 99.99
#3 2296 1178 5.38 1153 99.80 99.99
#4 2140 1178 5.88 836 99.63 99.87
#5 2717 1153 8.01 728 99.79 99.99
59
-
COMPUTATIONAL TEST-CASES
Volume-averaged and maximum
of reactions and nitric oxides rates
Case VALUEOverall NO rate,
kg/(m3s)
CH4 oxidation
rate,
kg/(m3s)
H2 oxidation
rate,
kg/(m3s)
#1Average 1.06 x 10-5 3.97 x 10
-13.46 x 10-5
Maximum 2.70 x 100 23.95 2.27 x 10-1
#2Average 9.64 x 10-5 3.09 x 10
-14.03 x 10-2
Maximum 4.27 x 10-2 5.82 28.49
#3Average 1.87 x 10-6 3.09 x 10
-14.03 x 10-2
Maximum 2.07 x 10-2 12.77 27.92
#4Average 1.48 x 10-6 2.15 x 10
-18.30 x 10-2
Maximum 1.42 x 10-2 14.28 23.46
#5Average 1.76 x 10-4 1.36 x 10
-14.90 x 10-2
Maximum 8.28 x 102 30.77 38.1360
-
Case#1
Temperature distributions in the combustor, K
Case#2
Case#3
Case#4
Case#5
61
-
Case#2
Case#3
Case#4
Case#5
Methane Reaction Rate Hydrogen Reaction Ratekg/(m3s)
62
-
H2 frompilot
NG frompremixer
Comparison between the species mass fraction when injecting H2 from pilot or premixer.
NG and H2 From premixer
63
-
Comparison between the reaction rates of H2when injected from the pilot or the premixer.
kg/(m3s)
64
-
Detailed chemistry and flamelet – pdf based approach may provide a
further proof: (TEMPERATURE DISTRIBUTIONS)
Grimech 3.0 and flameletReduced mechanisms and EDC67
-
68
Detailed chemistry and Detached Eddy Simulation (DES)
-
Detailed chemistry and Detached Eddy Simulation (DES)
69
Methane
Premixed CH4/H2 80%- 20%
Premixed CH4/H2 - Part Load
H2 From Pilot Line- Part Load
Methane
Premixed CH4/H2 80%- 20%
Premixed CH4/H2 - Part Load
H2 From Pilot Line- Part Load
-
70
-
authors’ papers:
-- CYCLE OPTIMIZATION AND COMBUSTION ANALYSIS IN A LOW-NOX MICRO-GAS TURBINETURBO-EXPO AND JRNL. OF GAS TURBINES AND POWER 2006
--NOX SUPPRESSION FROM A MICRO-GAS TURBINE APPROACHING THE MILD-COMBUSTION REGIME, TURBO-EXPO 2007
--COMBUSTION SIMULATION OF AN EGR OPERATED MICRO-GAS TURBINE TURBO-EXPO AND JRNL. OF GAS TURBINES AND POWER 2008
--CFD ANALYSIS OF THE FLAMELESS COMBUSTION IN A MICRO-TURBINE
TURBO-EXPO 2009
--COMPARISON OF EXTERNAL AND INTERNAL EGR CONCEPTS FOR LOW EMISSION MICRO GAS TURBINES. ASME TURBO EXPO 2010
-- LIQUID BIO-FUELS IN AN EGR EQUIPPED MICRO GAS TURBINE ASME TURBO EXPO 2011
--FUELLING AN EGR EQUIPPED MICRO GAS TURBINE WITH BIO-FUELS. ASME TURBO EXPO 2012
-- STUDY OF AN EXHAUST GAS RECIRCULATION EQUIPPED MICRO GAS TURBINE SUPPLIED WITH BIO-FUELS. APPLIED THERMAL ENGINEERING 2013
- COMBUSTION FEATURES OF A BIO-FUELLED MICRO-GAS TURBINE, APPLIED THERMAL
ENGINEERING , 2015
- CFD STUDY OF A MGT COMBUSTOR SUPPLIED WITH SYNGAS, ENERGY PROCEDIA, 2016
- INNOVATIVE COMBUSTION ANALYSIS OF A MICRO-GAS TURBINE BURNER SUPPLIED WITH
HYDROGEN-NATURAL GAS MIXTURES”. ENERGY PROCEDIA. 2017
- THERMAL CYCLE AND COMBUSTION ANALYSIS OF A SOLAR-ASSISTED MICRO GAS TURBINE.
ENERGIES 2017
- NUMERICAL INVESTIGATION OF SPRAY DEVELOPMENT IN A MICRO GAS TURBINE LPP
COMBUSTOR WITH AIRBLAST ATOMIZER. ASME TURBO EXPO 201871
-
72
A 100 kW MGT with Lean Premixed reverse flow combustor
-
73
EXPERIMENTAL EQUIPMENT
-
74
T100 COMBUSTOR
tetrahedral grid of 4.7 million of nodes
-
75
Flow Field inside the T100 Combustor
-
76
Methane – Hydrogen BlendsNovosellov and Malte + Jachimowski Schemes
-
77
Methane – Hydrogen BlendsTemperature Distributions
-
78
Methane – Hydrogen BlendsNitric Monoxide Distributions
-
79
Methane – Hydrogen BlendsReaction Rates
-
80
• di Gaeta, A., Reale, F., Chiariello, F., Massoli, P., 2017, "A dynamic model of a 100kW micro gas turbine fuelled with natural gas and hydrogen blends and its applicationin a hybrid energy grid", Energy, Volume 129, Pages 299-320
• Calabria, R. , Chiariello, F., Massoli, P., Reale, F., 2014, “Part load behavior of amicro gas turbine fed with different fuels”, ASME paper no. GT2014-26631
• Reale F., Iannotta V., Tuccillo R. ,“ Numerical Study of a Micro Gas TurbineIntegrated With a Supercritical CO2 Brayton Cycle Turbine", ASME paper no.GT2018- 76656
• Calabria, R. , Chiariello, F., Massoli, P., Reale, F., 2015, “CFD Analysis of TurbecT100 Combustor at Part Load by Varying Fuels”, ASME paper no. GT2015-43455
• Reale, F., Calabria, R., Chiariello, F., Pagliara, R., and Massoli, P., 2012, "A microgas turbine fuelled by methane-hydrogen blends", Applied Mechanics and Materials,232, pp. 792-796.
Papers on T100 Combustor form I.M. researchers
-
81
Thanks for your attention !!
mailto:[email protected]:[email protected]:[email protected]:[email protected]:[email protected]:[email protected]:[email protected]