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International Journal of Applied Engineering Research ISSN 0973-4562 Volume 11, Number 18 (2016) pp 9297-9306
© Research India Publications. http://www.ripublication.com
9297
Steam Boilers’ Advanced Constructive Solutions for the Ultra-supercritical
Power Plants
Nikolay Rogalev, Vadim Prokhorov, Andrey Rogalev, Ivan Komarov and Vladimir Kindra
National Research University “Moscow Power Engineering Institute”
Krasnokazarmennaya str. 14, 111250, Moscow, Russian Federation.
Abstract This paper presents possible construction solutions to new
steam boilers for ultra-supercritical power plants. At the current
stage of development science and technology, one of the main
problems with the transition to ultra-supercritical steam
parameters is that a nickel-rich refractory and high temperature
resistant steels and alloys prevail on weighting structure of
materials for the ultra-supercritical power plants. Two
advanced versions of boiler units’ arrangement allowing to
reduce the length of main steam piping and reheat piping are
selected: horizontal and M-type.
Optimal gas path geometry, arrangement of heating surfaces,
slag removal system has been designed and the length of main
steam piping and reheat piping has been estimated for the
considered solutions. When passing to horizontal arrangement,
the flow structure in boiler unit circuit changes significantly.
Therefore, for the given version the extension study of furnace
chamber aerodynamics, based on 3D modeling, was conducted.
The burner units arrangement was developed as well as the ash
hopper design that affects greatly aerodynamics.
New power plant arrangement with horizontal steam boiler has
been developed. If the solutions under consideration are used,
the length of the main steam piping could be reduced from 150
m to 70 m compared to tower-type arrangement.
Keywords: arrangement, horizontal boiler, ultra-supercritical
steam parameters, 3D modelling, furnace chamber
INTRODUCTION
The thermal efficiency improvement of a power plant depends
on an increase in the energy price and an attempt to decrease
the power generation cost as well as on the global climate
change threat resulting from a rapid growth of greenhouse gas
and pollutants emission into the atmosphere in the last 50 years.
In the foreseeable future, the fossil fuel will remain crucial in
power generation. Combined cycle power plants (CCPP) hold
leading position among the possible means of efficiency
improvement for the fossil-fuel power generation. The increase
of efficiency to 55-60 % has been obtained due to the increase
of steam initial temperature to 1500 ºС upstream of the gas
turbine. In the meantime, the initial steam temperature for
majority of the steam turbine units (STU) stands at 540-560 ºС.
As a result, the efficiency of steam turbine power plant (STPP)
stands at the level of 38-39 %. The efficiency of main and
auxiliary equipment of STPP is close to limiting value, that
prevents substantial efficiency improvement of the unit due to
further upgrading of equipment.
There are high chances that coal will remain one of the key
types of fossil fuel for thermal power plant (TPP) due to its
considerable reserves and low cost. Its share growth is
suggested in fuel balance. The popular means of emission
abatement as well as purification, utilization and disposal of
combustion products at the coal power plants are extremely
capital-intensive and energy-consuming. In most cases, they
double plant construction costs and consume about 10% of
energy output. Therefore, the efficiency improvement of the
energy production, leading to the polluting emissions’ decrease
due to less fuel consumption, is of key importance in coal
generation.
Thus, the raising of initial steam parameters is a key method of
the efficiency substantial improvement of the energy
production at STU.
At present, the development of the most advanced ultra-
supercritical power plants is in progress. Steam initial pressure
upstream of a turbine reaches 35 MPa, and its temperature is
equal to 700-720 ºС. The specified technology has not yet
reached the industrialization stage. Intensive work in this
direction is in progress in EU, USA, Japan and China. They
adopted special programs, determining the principal directions
for the development of ultra-supercritical power plants.
Steam superheat to 700-720 ºС with simultaneous raising of
pressure to 35 MPa allows to achieve power plant efficiency
factor about 49-51 % [1-3], that is close to efficiency factor of
CCPP with lower-temperature (about 1100 ºС) gases for the
present gas turbine units. Fig. 1 shows steam-turbine
technology evolution in relation to steam initial parameters,
corresponding values of the power plant efficiency and
construction material types used for high-temperature elements
production [4, 5].
Figure 1: STPP efficiency improvement at time scale with
class indication of materials in use
International Journal of Applied Engineering Research ISSN 0973-4562 Volume 11, Number 18 (2016) pp 9297-9306
© Research India Publications. http://www.ripublication.com
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Adoption of technology concerned directly depends on
generation of new refractory and high temperature resistant
materials, which would provide continuous safe operation of
equipment at high temperatures and pressures of a steam.
Note that the generation of new materials with required
properties provides only technical capability of practical
realization of power plant with ultra-supercritical steam
parameters. Not least important is the cost of such power
plants. It will be determined by the cost of high temperature
resistant materials in use. Change in price of the used
construction materials is shown in Fig. 2 [6], suggesting that
materials in operation at a temperature about 700 ºС are
presently more expensive than those used in units developed
with ultra-supercritical steam parameters.
Figure 2: Change in price of materials depending on working
temperature
Fig. 3 shows weighting structure of the used materials,
classified at different levels of initial parameters. [7].
Represented data testifies that when passing from supercritical
to ultra-supercritical steam parameters, a nickel-rich refractory
and high temperature resistant steels and alloys prevail on the
list of useable construction materials.
Figure 3: Weighting structure of materials in use depending on
steam initial parameters
Owing to high cost of the high temperature resistant materials
and their essential share within metal expenses, one of the key
directions for the development of power plants with ultra-
supercritical steam parameters is working-out of technical
solutions allowing to decrease the number of used expensive
steels and alloys while power plant equipment manufacturing,
therewith reducing the capital costs.
Fig. 4 shows diagram of distribution of high temperature
resistant materials over the main elements of power plant with
ultra-supercritical steam parameters [4]. It is apparent that most
of the nickel alloys are applied for high temperature main steam
and reheat piping. Therewith, about 20% of the cost of ultra-
supercritical power plant fall to share of steam-piping system
[6].
Figure 4: Conditional diagram of distribution of refractory and
high temperature resistant materials over the main elements of
power plant
Actually, when using tower-type boiler (Fig. 5), the length of
the main steam piping may be 150 m and more at power plant
with a capacity of 660-1000 MW. In this regard, the vital task
is to shorten the distance between the superheat outlet headers
and the inlet port of steam turbine.
Figure 5: Example of standard steam turbine and tower boiler
arrangements
It follows, that technical solutions, allowing to reduce the total
length of these lines, will considerably cheapen the
construction of power plants with ultra-supercritical steam
International Journal of Applied Engineering Research ISSN 0973-4562 Volume 11, Number 18 (2016) pp 9297-9306
© Research India Publications. http://www.ripublication.com
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parameters. The length of main steam piping and reheat piping
is determined by design of the main equipment – boiler and
turbine – and their relative position.
POSSIBLE CONSTRUCTION SOLUTIONS FOR BOILER
UNITS WITH ULTRA-SUPERCRITICAL STEAM
PARAMETERS
Considering that shortening of the main steam and reheat
piping appears to be the relevant objective in the result of
transition to a new working temperature level, developments in
this area were carried out back in the middle of the 20th century.
Boiler “PK-37” can be mentioned as an example of the first
arrangement solution. It was developed in the 60s at Machine
Engineering Plant in Podolsk (Fig. 6 [8]) and made as inverted
conventional arch boiler.
Figure 6: Inverted (U-shaped) boiler PK-37 arrangement:
sectional drawing:
1 – economizer; 2, 4 – transition section; 3, 5 – primary
superheater; 6 – convective superheater; 7 – platen superheater;
8 – lower radiant section; 9 – upper radiant section;
10 – division wall; 11 – turning chamber wall
At present time, Alstom Power Company works on a similar
project of power plant (Fig. 7).
Figure 7: Power plant arrangement with inverted boiler by
Alstom Power Company
Horizontal vertical tube boiler with horizontally-oriented
furnace chamber (Benson boiler) may serve as an example of
another approach implementation (Fig. 8).
Figure 8: The sectional drawing of horizontal Benson boiler
arrangement
Originally, the given solution was engineered for CCPP by
Siemens, but then the project was reoriented to building of a
power plant with steam parameters equal to 35 MPa, 700/720
ºС. Example of the power plant arrangement with such boiler
unit is shown in Fig. 9 [9].
Figure 9: The arrangement of power plant with horizontal
boiler
International Journal of Applied Engineering Research ISSN 0973-4562 Volume 11, Number 18 (2016) pp 9297-9306
© Research India Publications. http://www.ripublication.com
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Although both versions provide considerable length reduction
of high temperature pipelines, they have some disadvantages,
which make their maintenance difficult. Therefore, inverted
arrangement (Fig. 6 and Fig. 7) impedes combustion of coal
fuel that is the most perspective for ultra-supercritical power
plants. This is due to the fact that ash hopper is in the area of
primary superheater, and successive passage of two corners by
combustion products will inevitably deflect current lines,
potentially throwing them in ash hopper, what can lead to heat
loss and extra difficulties in providing bottom ash-handling
system. An additional point to emphasize is that inverted
conventional arch boiler has burner units located in the upper
part of boiler plant, which complicates the supply of pulverized
coal.
The horizontal arrangement of boiler unit does not have the
above-mentioned disadvantages, however, in this case ash and
slag removal is also more complicated than for standard design.
In order for ash to be removed effectively from boiler gas duct
(Fig. 8 and Fig. 9) lower furnace wall shall have a slope of 50-
60º, resulting in high-elevation furnace and terminal hea-ders,
what leads to increasing length of high temperature pipelines.
Creative approach to solving the problem of shortening the
main steam piping was made by the Chinese specialists. In
cooperation with Siemens Company, they developed a project
of split-level steam turbine plant, consisting of high-potential
(higher-level) and low-potential parts of STP (Fig. 10) [10].
The given steam turbine is designed for a power plant having a
capacity of 1350 MW with steam initial parameters equal to 30
MPa and 600 ºС. The distinctive feature of the given project is
the double resuperheat with the following parameters: 9.17
MPa/620 ºС during the first reheat and 2.25 MPa/610 ºС –
during the second reheat. Feed water temperature is equal to
310 ºС, condenser backpressure is 4 kPa. At these parameters,
efficiency factor is 48.92 % [10].
Figure 10: Split-level arrangement of steam turbine
In this case, sections of connecting steam pipelines are
considerably shortened and thus, pipe manifold cost declines
and loss of pressure reduces. However, the arrangement suffers
from a number of shortcomings. The main of them are the
necessity of steelwork hardening to install high-level turbine,
the necessity of applying of two generators, duplication of
control and lubrication system and other systems, maintenance
and repair complexity. All of these require technical and
economic analysis at subsequent stages of project
implementation.
Thus, although there is some development basis on the given
subject, the issue of optimal arrangement solution for power
plant boiler unit with ultra-supercritical steam parameters
remains relevant.
In order to beef up knowledge about possible construction
solutions concerning arrangement of steam boilers, thermal,
aerodynamic and design calculations of boiler unit different
versions were performed. Projecting was conducted for
Kuznetsk coal-fired (type D) power plant with a capacity of
1000 MW. These are critical parameters of the power plant
engineered: initial temperature and pressure are equal to 710 ºС
and 35 MPa respectively, single reheat is applied to 720 ºС at
a pressure of 7 MPa, feed water temperature is equal to 315 ºС,
condenser backpressure is 4 kPa. At these parameters, power
plant net efficiency is 51 %.
Following the elaboration, overall dimensions of steam boilers
were calculated. According to this information, a study of
possible arrangement solutions was undertaken. Table 1 shows
construction diagrams and length of pipelines for different
versions.
International Journal of Applied Engineering Research ISSN 0973-4562 Volume 11, Number 18 (2016) pp 9297-9306
© Research India Publications. http://www.ripublication.com
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Table 1: Alternative arrangement solutions for boiler and steam turbine plants with ultra-supercritical steam parameters
Conventional arch boiler, horizontal arrangement T-shaped boiler, horizontal arrangement
Live steam piping length: 53.8 m;
Reheat steam piping length: 51.9 m;
Total length: 105.7 m.
Live steam piping length: 68.8 m;
Reheat steam piping length: 82.2 m;
Total length: 150 m.
Conventional arch boiler, standard arrangement T-shaped boiler, standard arrangement
Live steam piping length: 96.2 m;
Reheat steam piping length: 81.6 m;
Total length: 177.8 m.
Live steam piping length: 106.2 m;
Reheat steam piping length: 81.6 m;
Total length: 187.8 m
Conventional arch boiler, inverted arrangement
(U-shaped)
T-shaped boiler, inverted arrangement
Live steam piping length: 36.6 m;
Reheat steam piping length: 43.4 m;
Total length: 80 m.
Live steam piping length: 36.6 m;
Reheat steam piping length: 50 m;
Total length: 86.8 m.
Tower-type boiler Horizontal boiler
Live steam piping length: 97.7 m;
Reheat steam piping length: 111.7 m;
Total length: 209.4 m.
Live steam piping length: 30.9 m;
Reheat steam piping length: 32.1 m;
Total length: 63 m.
International Journal of Applied Engineering Research ISSN 0973-4562 Volume 11, Number 18 (2016) pp 9297-9306
© Research India Publications. http://www.ripublication.com
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It follows as a consequence that change in boiler design
arrangement significantly affects the length of the main steam
piping. Among the considered versions, the maximum length
of pipelines is typical for tower boiler, and minimum length of
pipelines is typical for horizontal boiler. As a whole, inverted
arrangements appear perspective enough. For this reason, the
subject of further detailed research was focused on the given
conceptions.
M-TYPE BOILER UNIT WITH ULTRA-SUPERCRITICAL
STEAM PARAMETERS
As was shown, inverted arrangements provide considerable
length reduction of main steam piping and reheat piping.
However, it is reasonable to suppose that T-shaped
arrangement is the most favorably priced solution among all
inverted arrangements considered, since the burning of a large
amount of coal (incl. low-ash coal), the problem of erosive
wear of the heating surface becomes of key importance.
However, it is obvious that T-shaped arrangement requires
major optimization.
M-type boiler unit is the result of T-shaped boiler design
review. Structural shape of M-type boiler is shown in Fig. 11.
Applying of inverted furnace chamber assumes top-bottom
flow of flue gases. Burners and nozzles are located in the upper
third part of furnace, and the flue gas outlet – in its lower third
part. Such furnace chamber design allows to locate live steam
and reheat steam terminal headers significantly lower than in
standard boilers because of lower location of sloping gas ducts.
The primary and secondary superheaters are spaced between
two opposite sloping gas ducts, that provides for terminal
headers location nearly on the same level.
Figure 11: M-type boiler with ultra-supercritical steam parameters
Boiler is designed with a single furnace, turbine is installed
near boiler along the rear furnace wall, down and convection
passes. The proximity of terminal headers and turbine allows
to reduce the length of steam pipelines and total metal
consumption of a boiler. Superheater and reheater outlet
headers are designed underneath the sloping gas ducts, not in
the upper part.
The given solutions make it possible to decrease the installation
level of terminal headers from 70 m to 20 m, that provides the
total length reduction of steam pipelines 2.5-3 times compared
to inverted conventional arch arrangement of a boiler with the
same capacity.
Location of burners at the top of boiler furnace with flue gases
output at its bottom predetermines fuel particle residence time
expansion in furnace chamber, that leads to an increase in
degree of fuel burn-up and, as a result, to reduction of
combustibles content in slag and flue ash, i.e. combustible loss
is reduced.
We may refer to the advantages of М-type arrangement those
fact that its applying allows to reduce fly ash with flue gases
approximately by 15 % due to their separation upstream of gas
port and further flow through ash hopper, followed by
reduction of fly ash wear of the convective heating surfaces.
Compared to inverted conventional arch and tower-type
arrangements, the installation area of platen superheaters is
expanded as well.
Furnace chamber dimensions of М-type boiler in horizontal
section are 14640 × 26840 mm. Pulverized coal combustion
takes place within vertical vortex system. Sixteen pulverized-
coal burners with opposite-fired shifted arrangement are
located at two levels. Secondary air nozzles (16 pcs) are also
located at two levels: nozzles of the second level are installed
International Journal of Applied Engineering Research ISSN 0973-4562 Volume 11, Number 18 (2016) pp 9297-9306
© Research India Publications. http://www.ripublication.com
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downward, and nozzles of the first level are located opposite
and upward. Secondary air nozzles (8 pcs) with opposite
shifted arrangement are located at one level upward. Burners
and nozzles are located in such a way that every set of burners
and nozzles (2 pulverized-coal burners, 2 secondary air nozzles
and tertiary air nozzle) would create 2 opposite vertical
vortices. Pulverized-coal burners and air nozzles are installed
on the front and rear walls. Pulverized-coal combustion takes
place in vertical-horizontal tangential flame (Fig. 12). Eight
pairs of vertical vortices are formed on all fronts.
Figure 12: Straight-flow burners and nozzles arrangement at
M-type boiler with ultra-supercritical steam parameters in even
vertical sections of the furnace
Boiler is designed for bottom-ash removal: at the elevation of
11.15 m front and rear walls taper off at an angle 52º, forming
hopper work points.
At the bottom of furnace chamber, flue gases are divided into
two streams, either of which turns to sloping gas duct. Such gas
stream movement contributes to additional separation of ashes,
reducing fly ash. On sidewalls before turn to sloping gas ducts,
furnace walls form aerodynamic noses providing more
proportional sweep of high pressure and low pressure platen
superheaters.
Divided into two streams at furnace chamber outlet, flue gases
pass through sloping gas ducts. In the left sloping gas duct in
the direction of gases, 1st and 2nd stages of high pressure platen
superheater (live steam) are located in line. In the right sloping
gas duct in the direction of gases, low pressure platen
superheater (reheat steam, 2nd stage) and low pressure
convective superheater (3rd stage) are located in line.
Downstream of sloping duct, gases enter convective passes. In
the left convective pass in the direction of gases, five
economizer tube banks are located. In the right convective pass
in the direction of gases, regulated stage of low pressure
convective superheater (1st stage) and four economizer tube
banks are located. Stringed tubes of economizer and outlet
tubes are located in turning chamber. Due to different number
of economizer tube banks at left and right part of down taking
duct, identical heat absorption can be achieved in both gas
ducts. Then flue gases pass three re-generative air heaters in a
parallel way.
Boiler is designed as gas-tight. The gas-tightness of furnace
chamber is provided by membrane walls. Also walls of sloping
gas ducts, turning chamber and convective pass, and
economizer tube banks are screened with membrane panels.
According to calculations, boiler gross efficiency is 93.07 %,
and estimated fuel consumption – 91.13 kg/s.
HORIZONTAL BOILER WITH ULTRA-SUPERCRITICAL
STEAM PARAMETERS
The second long-term construction solution to reduce the
length of steam pipelines is the horizontal arrangement of a
boiler unit. In this regard, the detailed research and engineering
study of the given version were conducted. Engineering study
of horizontal steam boiler was also conducted for power plant
with ultra-supercritical steam parameters having nominal
capacity of 1000 MW.
Combustion products flow over the heating surface is ordinary.
Flue gases downstream of furnace, successively pass over
platen superheater, primary superheater, the second and the
first stages of reheater, economizer and regenerative air heater.
Principal organization scheme of gas circuit with indication of
temperatures is shown in Fig. 13.
Compared to classic arrangement, the developed boiler unit has
a distinctive feature of slag removal arrangement, with ash
hoppers located along the full length of furnace chamber, what
exerts a significant impact on flow structure in boiler furnace.
In the course of boiler unit design research, three tasks
concerning furnace volume were completed: optimal position
in terms of flow structure and angle of slope for burner units
were determined; new construction of ash hoppers was
presented, providing minimum draft-pressure drop; unique
design of gas duct turn after furnace chamber was worked out,
providing minimum velocity profile variation after turn to
reduce non-uniform heat flow distribution over economizer
heating surface. In order to tackle the given issues 3D modeling
technologies were applied. Software application ANSYS CFX
was used for modeling.
International Journal of Applied Engineering Research ISSN 0973-4562 Volume 11, Number 18 (2016) pp 9297-9306
© Research India Publications. http://www.ripublication.com
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Figure 13: Principal organization scheme of gas circuit of horizontal boiler
In terms of numerical study, different structural variations of
the horizontal boiler were examined. The following parameters
varied: turn shape, furnace chamber dimensions, burner units
location, ash hopper shape. Fig. 14 shows two versions of
horizontal boiler with different shape of ash hopper and burners
location.
Figure 14: 3D models of horizontal boiler versions
Experimental modelling of the combustion process in furnace
is very expensive. On the other hand numerical investigation of
such complicated process requires validation experiments [11-
18]. Pre-assessment of furnace aerodynamic efficincy could be
done without firing by aerodynamic venting of the boiler flow
path. Calculations showed that in-line arrangement of ash
hoppers along furnace chamber allows to align vortex
formation and achieve its stability. Fig. 15 shows current lines
for the variant under consideration.
Figure 15: Aerodynamic 3D modeling results of furnace chamber
International Journal of Applied Engineering Research ISSN 0973-4562 Volume 11, Number 18 (2016) pp 9297-9306
© Research India Publications. http://www.ripublication.com
9305
Changes in vortex formation are shown in Fig. 16, with indication of the vector velocity field in three different sections along the
length of furnace chamber.
1st level of burners 3rd level of burners 4th level of burners
Figure 16: Vector velocity fields in three sections along the length of furnace chamber of horizontal boiler
Taking into account heat-recovery surfaces, the total length of
a boiler unit reaches 85.5 m; construction area required for its
installation is nearly twice the size of classic arrangements.
Therewith, terminal headers reach 34.5 m, providing length
reduction of high temperature pipelines almost by half. Apart
from that, there is a possibility of terminal headers lead to the
lower part of tube banks of convective heat-transfer surfaces,
so that they reach the level of 16 m. In this case, the total length
of main steam piping and reheat piping are shortened almost
four times compared to classic design of a boiler unit. Thus,
horizontal boiler unit makes it possible to reduce the share of
capital costs, which falls on high temperature pipelines, to 25
% of the initial share, providing cost reduction of the whole
power plant by 10-12 %.
Three-dimensional aerodynamic and one-dimensional heat and
hydraulic calculations showed the perspective of the given
design arrangement. Boiler efficiency reached 93.1 %.
The developed basic mutual arrangement of boiler and steam
turbine is shown in Fig. 17.
Figure 17: Power plant arrangement with horizontal steam boiler
Turbine unit is to be located along the boiler nearby its
superheater surfaces. This solution allows to reduce the length
of the main steam piping from 150 m to 70 m compared to
tower-type arrangement.
CONCLUSION
One way to improve economic feasibility of change-over to
ultra-supercritical steam parameters for coal-fired power plants
is the revision of series of fundamental construction solutions.
Almost 20% of overall cost of power plant with ultra-
International Journal of Applied Engineering Research ISSN 0973-4562 Volume 11, Number 18 (2016) pp 9297-9306
© Research India Publications. http://www.ripublication.com
9306
supercritical steam parameters fall on the steam pipelines. It is
demonstrated that changes of the boiler unit structural shape,
and mutual arrangement mode of the main equipment
determine the length of steam pipelines. Thus, the length of
main steam piping and reheat piping can be greater than 150 m
for power plants having a capacity of 600 MW or higher with
classic tower-type boilers. By contrast, when changing boiler
unit arrangement it is possible to shorten the distance from
superheater headers to turbine steam inlet more than two times.
In this paper two versions of a boiler unit are presented: М-type
and horizontal. Both constructions provide considerable length
reduction of the main steam pipelines (from 150 m to 50-70 m).
When passing to horizontal arrangement, the flow structure in
boiler unit circuit changes significantly. Therefore, for the
given version the extension study of furnace chamber
aerodynamics, based on 3D modeling, was conducted. Burner
units arrangement was developed as well as the ash hopper
design that affects greatly aerodynamics.
Heat and aerodynamic calculations proved high efficiency of
the solutions proposed. Efficiency of both boiler unit versions
(М-type and horizontal) exceeds 93 %.
ACKNOWLEDGEMENTS
The research has been carried out in the Moscow Power
Engineering Institute with financial support from the Russian
Federation represented by the Ministry of Education and
Science of the Russian Federation under Agreement
No.14.574.21.0098 on Grant Provision dated August 22, 2014,
for the purpose of implementation of the Federal Target
Program “Research and Development in Priority Growth Fields
of Russian Science and Technology Sector for 2014-
2020”.Unique identifier of the applied research:
RFMEFI57414X0098.
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