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Combustion Emissions from NH3 Fuel
Gas Turbine Power Generation Demonstrated
O. Kurata1*, N. Iki1, T. Inoue1, T. Matsunuma1,
T. Tsujimura2, H. Furutani2, H. Kobayashi3, A. Hayakawa3
1National Institute of Advanced Industrial Science and Technology (AIST), Japan2The Fukushima Renewable Energy Institute, AIST (FREA), Japan3Tohoku University, Japan
2017 AIChE Annual Meeting
October 29 – November 3, 2017, Minneapolis, MN, USA
Topical Conference NH3 Energy+ - Enabling Optimized, Sustainable Energy and Agriculture
560a NH3 Fuel End Use
• To protect against global warming, a massive influx of renewable energy is expected.
• Although hydrogen is a renewable media, its storage and transportation in large quantity
has some problems.
• Ammonia, however, is a hydrogen energy carrier and carbon-free fuel, and its storage and
transportation technology is already established.
• As ammonia utilization, ammonia combustion and ammonia fuel cell are expected.
2
Transportation Storage
NH3 production using renewable energy
C T
Combustor
Gen.
NH3 comb.
NH3
NH3 as a hydrogen energy carrier
SL of NH3-air laminar premixed flame
(Hayakawa,2015)
NH3-air combustion
• NH3-air combustion is difficult because the laminar burning velocity is much lower than that
of conventional hydrocarbon fuels.
• In 1967, Pratt examined an NH3-fired gas-turbine combustor, and concluded that
combustion efficiencies were unacceptably low.
• Verkamp showed that the pre-cracking of NH3 and the additives improved the flame stability
• Because of those difficulties, the research and development of NH3-fueled gas turbines were
abandoned, and it has not been retried until recently.
3
Solar model T-350 engine (Solar, Final Technical
Report, DA-44-009-AMC-824, 1968)
Recent work of NH3 fueled gas turbine
• Recent demand for hydrogen energy carrier revives the interest of NH3 fuel.
• Evans proposed NH3-air combustion gas turbine using pre-cracked NH3.
• Valera tested NH3-CH4-air gas turbine combustors.
• AIST successfully performed ammonia-kerosene co-fired gas turbine power generation in
2014, and ammonia-fired gas turbine power generation in 2015.
• AIST plans developing a low NOx combustor using combustor test rig.
• Since emission characteristics of test rig combustor differ from that of gas turbine, emission
data of gas turbine re-characterized with the other parameters is needed.
4
NH3-kerosene-air micro gas turbine in our
institute (AIST)NH3-air combustion gas turbine (Evans, 2013)
Emissions of NH3 and NOx
• In the case of NH3-air combustion, most products are N2 and H2O.
• Small amounts of NH3 and NO are detected as pollutant emissions.
• If the emission of unburnt NH3 increases, combustion efficiency decreases; this is
prone to occur because the laminar burning velocity of NH3-air pre-mixture is very
low. Combustion efficiency had been unacceptably low in the 1960s.
• In order to improve combustion efficiency, unburnt NH3 must be minimized.
• The emission of NOx is thought to increase because NH3 is the source of fuel-NO.
• A small amount of NH3 has been used for additives to study combustion chemistry
of NOx formation.
5
NH3,
AirCombustion
N2, Pollutant emissions
H2O, NH3, NO, …
Unburnt NH3 ↓ → Combustion efficiency ↑
NH3 fuel → Source of fuel-NO
6
Gas turbine
Loading equipment
Gas compressor SCRVaporizer NH3 1ton cylinder
Gas turbine power generation demonstrated
Ammonia 1ton cylinder
VaporizerFuel gas compressor
50kW gas turbine
SCR
FTIRPortable gas analyzer
Methane cylinders
Kerosene tank
Heated probe
Fig. 1 Schematic of ammonia combustion gas turbine power plant
Loading equipment
• The demonstration
facility consists of an
NH3 fuel-supply system,
NH3 gas compressor,
50 kWe-class micro gas
turbine, SCR NOx-
reduction apparatus,
and loading equipment.
Regenerator-heated gas turbine
• Micro gas turbines utilize a regenerative heat exchanger to improve the thermal
efficiency of the gas turbine cycle.
• Regenerative heat exchangers transfer exhaust heat after the turbine into combustion
air after the compressor.
• Thus, the combustor inlet temperature increases to around 500 °C.
• This high combustor inlet temperature enhances the flame stability of NH3-air
combustion and reduces the unburnt NH3.
7
Fig. Heat-regenerative-cycle gas turbine
Combustor
8
• A diffusion-type combustor was employed with the expectation of
realizing a higher flame stability.
• NH3 gas was injected from 12 holes located around the kerosene
injector, and an air swirler was positioned around the NH3 gas-injection
holes.
Prototype NH3 fueled gas turbine combustor
238mm
12
8m
m
Emission after SCR
• NOx reduction equipment using SCR was placed after the micro gas turbine.
• The NH3 addition to the SCR for NOx reduction was carried out in the piping, after the
micro gas turbine combustor.
• Although NOx emission after the micro gas turbine combustor is sufficiently high, the
SCR NOx reduction equipment can reduce it below the regulation limit
9
Fig. NOx emission after the SCR
Combustion emissions from gas turbine
• Although NOx emission after SCR is below the regulation limit, the NOx
emission from a micro gas turbine combustor is so high that it requires a
large-size SCR.
• If a low NOx combustion method is developed, the size of the facility could
be reduced.
• In order to achieve low NOx combustion, a combustor test rig was built in
the same place with a common NH3 fuel supply facility.
• Meanwhile, in the gas turbine, the results arise from the restriction of the
eigen balance of fuel, air, and heat, because the compressor and turbine
are connected by a single shaft.
• It is difficult to characterize combustion emissions from the combustor test
rig with the former parameters because there is no restriction of the quantity
of fuel, air, and combustor inlet temperature.
• Thus, this paper reports combustion emissions of the NH3 fuel gas turbine
before SCR, re-characterized with the other parameters, such as fuel flow
rate, overall equivalence ratio, combustor pressure, and combustion
temperature.
10
Eigen balance of fuel and air
• Meanwhile, in the gas turbine, the results arise from the restriction of the eigen
balance of fuel, air, and heat, because the compressor and turbine are connected by
a single shaft.
• It is difficult to characterize combustion emissions from the combustor test rig with
the former parameters because there is no restriction of the quantity of fuel, air, and
combustor inlet temperature. 11
0
500
1000
1500
0 100 200 300
ow70000rpm
ow72000rpm
ow75000rpm
ow78000rpm
ow80000rpm
Heat input LHV [kJ/s]
Air [m
3/h
]
Combustor with observation window (ow)
NH3-air combustion
Gas turbine
Test rig
Former reports on emissions
• In the case of NH3-air combustion, the NH3 and NO emissions strongly
depend on the combustor inlet temperature.
• In the case of CH4-NH3-air combustion, the emissions depend on the NH3
ratio.
12
0
500
1000
1500
2000
2500
3000
400 500 600 700
ow70000rpm
ow75000rpm
ow80000rpm
ow70000rpm
ow75000rpm
ow80000rpm
Combustor inlet temperature CIT [℃]
NH
3,
NO
(16%
O2)
[ppm
]
NH3
NO
Combustor with observation window (ow)
NH3-air combustion
0
500
1000
0
500
1000
1500
2000
0.0 0.5 1.0
NO
CIT
NO2
N2O
NH3
NO
(16%
O2)
[ppm
]
Com
busto
r in
let te
mpera
ture
CIT
[℃
]
NH3 ratio NH3_LHV / (CH4+NH3_LHV)
Combustor with observation window (ow)
CH4-NH3-air combustion
Electric power output: 31.4 kWe
Rotating speed: 75000 rpm
NH
3,
NO
2, N
2O
(16%
O2)
[ppm
]
NO2 and N2O emissions
• The global warming potential (GWP) of N2O is 298, and thus, N2O emission
needs to be minimized.
• The N2O emission decreases with increase of combustor inlet temperature,
i.e., electric power output, and stays below 46 ppm at a combustor inlet
temperature of 560 °C.
13
0
60
120
0
300
600
400 450 500 550 600 650
ow70000rpm
ow75000rpm
ow80000rpm
ow70000rpm
ow75000rpm
ow80000rpm
Combustor inlet temperature [℃]
N2O
(
16
% O
2)
[
pp
m]
NO
2(1
6%
O2)
[
pp
m]
NO2
N2O
Combustor with observation window (ow)
NH3-air combustion
Combustion emissions re-characterized
with the other parameters
• The emissions of NO and NH3 characterized by the fuel flow rate show one set of
emission pattern repeated in three heat input ranges.
• The overall equivalence ratio for 70000, 75000, and 80000 rpm were in the range
0.107–0.137, 0.117–0.157, and 0.132–0.142, respectively, which have overlaps.
• It is shown that the equivalence ratio alone does not determine the combustion
emissions.
14
0
500
1000
1500
2000
2500
3000
100 150 200 250 300
ow70000rpm
ow75000rpm
ow80000rpm
ow70000rpm
ow75000rpm
ow80000rpm
Heat input LHV [kJ/s]
NH
3,
NO
(1
6%
O2)
[pp
m] NH3
NO
Combustor with observation window (ow)
NH3-air combustion
0
500
1000
1500
2000
2500
3000
0.1 0.15 0.2
ow70000rpm
ow75000rpm
ow80000rpm
ow70000rpm
ow75000rpm
ow80000rpm
Overall equivalence ratio Φ
NH
3,
NO
(1
6%
O2)
[pp
m]
NH3
NO
Combustor with observation window (ow)
NH3-air combustion
Combustion emissions re-characterized
with the other parameters
• The combustor pressures for 70000, 75000, and 80000 rpm were in the range 285–292, 327–
337, and 369–371 kPa abs, respectively.
• It shows one set of emission patterns repeated in three pressure ranges.
• The temperature of the combustor liner is dependent upon the temperatures of the combustor
inlet and combustion.
• Although the dependency is most apparent in the former reports on emissions, it arises from the
eigen balance of fuel, air, and heat.
• It is expected that the accuracy of the results can be improved in the future combustor rig tests.
15
0
500
1000
1500
2000
2500
3000
250 300 350 400 450
ow70000rpm
ow75000rpm
ow80000rpm
ow70000rpm
ow75000rpm
ow80000rpm
Combustor pressure abs [kPa]
NH
3,
NO
(16%
O2)
[ppm
]NH3
NO
Combustor with observation window (ow)
NH3-air combustion
0
500
1000
1500
2000
2500
3000
600 700 800 900
ow70000rpm
ow75000rpm
ow80000rpm
ow70000rpm
ow75000rpmow80000rpm
Combustor liner temperature [℃]
NH
3,
NO
(1
6%
O2)
[pp
m]
NO
NH3
Combustor with observation window (ow)
NH3-air combustion
Acknowledgement
• This work was supported by the Council for Science, Technology and Innovation (CSTI), the
Cross-ministerial Strategic Innovation Promotion Program (SIP), “Energy Carriers” (Funding
agency: Japan Science and Technology Agency (JST)).
• The authors also thank “Toyota Turbine and Systems Inc.” for their assistance with the
operation of the micro gas turbine system.
16
Thank you for your attention !!
17