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Recent Developments in Small Industrial Gas turbines Ian Amos Product Strategy Manager Siemens Industrial Turbomachinery Ltd Lincoln, UK
Copyright © Siemens AG 2009. All rights reserved.
Content
Gas Turbine as Prime Movers Applications History
Technology thermodynamic trends and drivers core components
Future requirements Market developments
Page 2
Nov 2010
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Gas Turbine as Prime Mover Prime mover : A machine that transforms energy from thermal, electrical or pressure form to mechanical form; typically an engine or turbine. Gas Turbines vary in power output from just a few kW more than 400,000 kW. The shaft output can be used to generate electricity from an alternator or provide mechanical drive for pumps and compressors. Page 3
Copyright © Siemens AG 2009. All rights reserved. Energy Sector
Nov 2010
Siemens Industrial gas turbine range Utility Turbines
Figures in net MW
SGT5-8000H
375
SGT5-4000F
287
SGT6-8000H
266
Industrial Turbines
SGT6-5000F SGT5-2000E SGT6-2000E SGT-800 SGT-700 SGT-600 SGT-500 SGT-400 SGT-300 SGT-200 SGT-100
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198 168 113 47 31 25 17 13 8 7 5
Nov 2010
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Industrial Gas Turbine Product Range Portfolio (MW)
SGT-100-1S
47 SGT-800 30 SGT-700 SGT-600 25 SGT-500 17 SGT-400 13 SGT-300 8 SGT-200 7 SGT-100 5
SGT-100-2S
SGT-200-2S
SGT-200-1S
SGT-300
SGT-400
SGT-500
Page 5
SGT-600
Nov 2010
SGT-700
SGT-800
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Industrial Gas Turbine Product applications Power Generation
Pumping
An SGT-100 generating set is installed on Norske Shell's Troll Field platform in the North Sea
Thirty SGT-200 driven pump sets on the OZ2 pipeline operated by Sonatrach, Algeria
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Nov 2010
Compression
Two SGT-700 driven Siemens compressors for natural gas liquefaction plant owned by UGDC at Port Said, Egypt.
CHP
Comb. Cycle
An SGT-800 CHP plant for InfraServ Bavernwerk’s chemical plant in Gendork, Germany.
Two SGT-400 generating sets operating in cogeneration/ combined cycle for BIEP at BP’s Bulwer Island refinery, Australia
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Gas Turbine Refresher Comparison of Gas Turbine and Reciprocating Engine Cycle AIR INTAKE
FUEL
COMBUSTION EXHAUST
COMPRESSION
Continuous
Intermittent AIR/FUEL INTAKE Page 7
COMPRESSION
Nov 2010
COMBUSTION
EXHAUST
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Gas Turbine as Prime Mover
Gas Turbine Characteristics Size and Weight High power to weight ratio giving a very compact power source
Operation and Maintenance No Lubricating oil changes High levels of availability
Vibration Rotating parts mean vibration free operation requiring simple foundations
Fuel flexibility Dual fuel capability Burn Lean gases (high N2 or CO2 mixtures) Varying calorific values
Emissions Very low emissions of NOx Page 8
Nov 2010
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Brayton Cycle
1-2 2-3 3-4
Air drawn from atmosphere and compressed Fuel added and combustion takes place at constant pressure Hot gases expanded through turbine and work extracted
(in single shaft approx 2/3 of turbine work is used to drive the compressor) Copyright © Siemens AG 2009. All rights reserved. Energy Sector
Nov 2010
Page 9
Ideal Engine Cycle: Efficiency
Ideal thermal efficiency
1 Simple cycle efficiency = 1 − P1 P2
( γ −1) / γ
Cycle efficiency is therefore only dependant on the cycle pressure ratio. Assumption : Ideal cycle with no component or system losses.
0.7 0.6 0.5 0.4 0.3 0.2 0.1 0 0
10
20
30
40
50
Pressure Ratio Page 10
Nov 2010
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Engine Cycle: The Real Engine Deviations from Ideal Cycle
‘Real’ Efficiencies
•Aerodynamic losses in turbine and compressor blading
• Practical simple cycle gas turbines achieve 25 to 40 % shaft efficiency
• Working fluid property changes with temperature • Pressure losses in intakes, combustors, ducts, exhausts, silencers etc.
• However, heat rejected in the exhaust can be used :-
• Air used for cooling hot components • Parasitic air & hot gas leakages • Mechanical losses in bearings, gearboxes, seals, shafts • Electrical losses in alternators Page 11
• Complex gas turbine cycles can achieve shaft efficiencies up to 50%
•Large combined cycle GT can achieve close to 60% shaft efficiency •Cogeneration (Heat and Power) can exceed 80% total thermal efficiency Copyright © Siemens AG 2009. All rights reserved. Energy Sector
Nov 2010
Energy Cost Savings GT cycle parameter study 43.0 25
42.0
Shaft Efficiency (%)
22
41.0 20
40.0
18
39.0
PRESSURE RATIO
16
38.0 14
37.0 1300ºC
1350ºC
1400ºC
1450ºC
1250ºC
36.0 1200ºC
FIRING TEMPERATURE
35.0 280 290 300 310 320 330 340 350 360 370 380 390 400 410 420 430 440 450 460 470 480 Shaft Specific Output (kJ/kg)
Increase Pressure ratio and firing temperatures for higher simple cycle efficiencies Page 12
Nov 2010
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Design Drivers : Low Specific Fuel Consumption Higher Pressure Ratios • Increased Cycle Efficiency • Increased number of compressor / turbine stages and therefore cost Complex Cycles • Increased Cycle Efficiency and/or Specific Power • Can impact operability, cost and reliability Higher Firing Temperature • Requires increased sophistication of cooling systems • Can impact life and reliability and combustor emissions
Page 13
Nov 2010
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Design Drivers : Availabilty, Cost and Emissions High reliability. Moderates the trend to increase firing temperature and cycle complexity. Low Emissions (Driven by environmental legislation) More difficult to achieve with high firing temperatures and combustion pressures Lowest possible cost. Encourages smallest possible frame size, i.e. high specific power high firing temperature. Reduced Pressure ratios (< 20:1) to avoid auxiliary fuel compression costs
Compromise is required in the concept design to get the best balance of parameters Page 14
Nov 2010
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Future Machines
SGT-400
SGT-300
TB
TD
TG
TF
TE
TA
16 15 14 13 12 11 10 9 8 7 6 5 4 3
1300 ttiioo RRaa rree u u s s
es Pr
1200
urree
t aatu eerr mpp eem T T g
1100
inng FFiir
1000 900 800
Firing Temperature °C
Pressure Ratio
3CT
Centrifugal Compr.
SGT-100
SGT-200
Core Engine Trends: Key Parameter Trends
700 1950
1960
1970
1980
YEAR Year
2000
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Nov 2010
Page 15
1990
Engine Trends: Thermal Efficiency 40 SGT-400
38
300 36 34
250
SGT-100
32
SGT-200
200
Specific Power Output Thermal Efficiency
150 TB5000
30
Thermal Efficiency (%)
Specific Power (kJ/kg)
350
28 26
100 1975
1980
1985
1990
1995
2000
24 2005
Year
Dramatic impact of increased TET and pressure ratio over last 25 years:
• • • Page 16
Specific Power increased by almost 100% Specific Fuel Consumption reduced by over 30% reduced airflow for a given power output and has resulted in smaller engine footprints, reduced weight and reduced engine costs Nov 2010
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Product Evolution
SGT-300 Introduced 1995 7,900 kWe 30.5% eff
TA Introduced 1952 750kW
17.6% eff
Developed to 1,860kW
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Nov 2010
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Gas Turbine Layout - single shaft or twin shaft
Single Shaft Expansion through a single series of turbine stages. Power transmitted through rotor driving the compressor and torque at the output shaft
Twin Shaft Expansion over 2 series of turbines. Compressor Turbine (CT) provides power for compressor Useful output power provided by free Power Turbine (PT) Page 18
Nov 2010
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SGT-400 Industrial gas turbine
Compressor
Page 19
Combustion system
Nov 2010
Gas Generator Turbine
Power Turbine
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Combustion
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Environmental Aspects Pollutants and Control Pollutant
Effect
Method of Control
Carbon Dioxide
Greenhouse gas
Cycle Efficiency
Carbon Monoxide
Poisonous
DLE System
Sulphur Oxides
Acid Rain
Fuel Treatment
Nitrogen Oxides
Ozone Depletion Smog Poisonous Greenhouse gas Visible pollution
DLE System
Hydrocarbons Smoke
DLE System DLE System
DLE - Dry Low Emissions
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Nov 2010
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Exhaust Emission Compliance Emissions control: Two types of combustion configuration need to be considered: Diffusion flame Dry Low Emissions (DLE or DLN) using Pre-mix combustion
Diffusion flame Produces high combustor primary zone temperatures, and as NOx is a function of temperature, results in high thermal NOx formation Use of wet injection directly into the primary zone to lower combustion temperature and hence lower NOx formation
Dry Low Emissions Lean pre-mixed combustion resulting in low combustion temperature, hence low NOx formation With good design and control <25ppm NOx across a wide load and ambient range possible Page 22
Nov 2010
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Combustion NOx Formation 1000
NOx Formation Rate [ ppm/ms ]
100 10 1 0.1
Diffusion Flame
0.01 0.001
Lean Pre-mix 0.0001 0.00001 0.000001 1300
1500
1700
1900
2100
2300
2500
Flame Temperature [ K ]
Flame temperature affects thermal NOx formation Page 23
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Nov 2010
Combustion NOx Formation Flame Temperature as a function of Air/Fuel ratio Diffusion flame reaction zone temperature
Lean burn
Flame temperature
Diffusion flame
Lean Pre-mixed (DLE/DLN)
Lean
Page 24
Nov 2010
Stoichiometric FAR
Rich
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Combustor Configuration NOx product is a function of temperature
Diffusion Combustion - high primary zone temperature
Cooling
Dry Low Emissions Combustion -low peak temperature achieved with lean pre-mix combustion Page 25
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Nov 2010
DLE Lean Pre-mix Combustor (SGT-100 to SGT-400 configuration) Igniter
Liquid Core
Pilot Burner
Main Burner Radial Swirler
Robust design involving no moving parts Fixed swirler vanes Variable fuel metering via pilot and main fuel valves
Main Gas Injection Igniter
Pilot Gas Injection
Pre Chamber
Air
Gas/Air Mix
Gas
Air Double Skin Impingement Cooled Combustor
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Nov 2010
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Lean Pre–Mix combustion Simple fuel system Variable fuel metering via pilot and main fuel valves Low NOx across a wide operating range of load and ambient conditions BLOCK VALVE
BLOCK VALVE
M
MAIN FLOW CONTROL VALVE
MAIN MANIFOLD BLEED VALVE
PILOT MANIFOLD PILOT FLOW CONTROL VALVE
Page 27
Nov 2010
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Combustion DLE Lean Premix System
Key to success good mixing of fuel and air multiple injection ports around swirler
long pre-mix path fuel injection as far from combustion zone as possible
good air flow distribution can annular arrangement with top hats
use of pilot burner CO control & flame stability
use of guide vane modulation/air bleed air flow management
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Nov 2010
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DLE System : Siemens experience
15million operating hours across the range (SGT-100 to SGT-800) Approximately 1000 DLE units About 90% of new orders DLE
Page 29
Nov 2010
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Experience Stable load accept/reject Daily profile for unit running more than 8000hrs DLE operation on liquid fuel.
kW
Daily variations Load Shed and Accept
Page 30
Nov 2010
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Gas Fuel Flexibility BIOMASS & COAL GASIFICATION
3.5
Other gas
High Hydrogen Refinery Gases
Associated Gas
37
Landfill & Sewage Gas
49
65 LPG
Siemens Diffusion IPG Ceramics
Off-shore lean Well head gas
Operating Experience
Off-shore rich gas
Siemens DLE Units operating DLE Capability Under Development Pipeline Quality NG Low Calorific Value (LCV)
Medium Calorific Value (MCV)
10
20
‘’Normal’’
30 40 50 Wobbe Index (MJ/Nm³)
60
SIT Ltd. Definition
70
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Nov 2010
Page 31
High Calorific Value (HCV)
The change in WI by the addition of inert species to pipeline quaility gas
50 UK Natural Gas
45
CO2 N2
Wobbe MJ/m
3
40 35 Medium CV Fuel
30
MCV Rangedevelopment Definition
25 20 15 10 5
LCV Burner
0 0
10
20
30
40
50
60
70
80
90
100
CO2 or N2 content of UK Natural Gas Page 32
Nov 2010
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Examples of Siemens SGT Fuels Experience NON DLE Combustion Natural Gas Wellhead Gases Landfill Gas Sewage Gas High Hydrogen Gases Diesel Kerosene LPG (liquid and gaseous) Naphtha ‘Wood’ or Synthetic Gas Gasified Lignite
Sewage gas standard burner Gasified Biomass Special Diffusion burner
5
10
Landfill gas Special Diffusion burner
15
20
25
High Hydrogen gas standard burner UK Natural Gas
30
35
40
45
50
Liquified Petroleum gas modified MPI
55
60
65
70
Wobbe Index MJ/m3 standard gases
Gaseous Fuel Range of Operation
DLE experience on Natural Gas, Kerosene and Diesel DLE on fuels with high N2 and CO2 content. DLE Associated or Wellhead Gases Page 33
Nov 2010
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Turbine
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Aerodynamic optimised design !
Minimised loss optimum pitch/width ratio across whole span. low loading
High speed
high stage number
low Mach numbers thin trailing edges low wedge angle zero tip clearance Page 35
Nov 2010
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Aerodynamics High Load Turbine
Computational Fluid Dynamics (CFD) used to complement experimental testing of advanced components. Page 36
Nov 2010
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Analytical optimised design !
Reduce blade stresses Minimal shroud
shroud may still be desirable for damping purposes.
High hub/tip area ratio Low rotational speed. Maximise life Low temperatures Low unsteady forces Page 37
Nov 2010
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Mechanical Design Improved analysis software (grid and solver) and improved hardware allow traditional ‘postdesign’ to be carried out during design iterations. Meshing of complex cooled blade could take many man months in early 90’s - now down to minutes. More sophisticated analysis for detailed lifing studies still required after design.
Page 38
Nov 2010
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Fatigue Life of Rotating Blades Positions of Concern
Blade Vibration response Predicted by FE and measured in Lab. Identifies critical blade frequencies and modes (Campbell Diagram)
Aerofoil
High Cycle Fatigue Fillet Radii between aerofoil & platform Top neck of firtree root
Fillets
Low Cycle Fatigue In areas of highest stress Eg - blade root serrations Root Serration (including skew effects) Copyright © Siemens AG 2009. All rights reserved. Energy Sector
Nov 2010
Page 39
Mechanical Design - Vibration analysis Campbell Diagram for LPT Blade (Blade only) EO20
6000
EO18
EO19
EO17
mode 6
EO11 EO10
3000
mode 4
EO9
mode 3 EO6
2000
mode 2
1000
mode 1
0 15000
15500
Iteration 3 version 10
Page 40
100%
4000
105%
mode 5
95%
Frequency (Hz)
5000
Nov 2010
EO3
16000
16500
17000
17500
18000
Engine Speed (rpm)
18500
19000
19500
20000
D G Palmer 3-8-01
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Cooling optimised design !!
Large LE radius minimise stagnation htc thick trailing edge thickness and large wedge angle for cooling thickness distribution to suit cooling passages. Minimise gas washed surface.
Page 41
Nov 2010
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Cooled Blading Designs SGT100 > SGT300 > V2500 Aeroengine
Page 42
Nov 2010
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SGT400 First Vane Cooling Features
Impingement Cooling
Film Cooling Turbulators
Cast 2 Vane Segment
Page 43
Nov 2010
Trailing Edge Ejection
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SGT-400 13MW Industrial Gas Turbine First Stage Cooled Vane Hot Blades are life limited. -Oxidation - Thermal fatigue - Creep
Life typically 24,000 hrs. Life can be increased or decreased depending on duty and environment. Page 44
Nov 2010
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SGT-300 First Stage Cooled Rotor Blade Ceramic Core forming Cooling Passages
Page 45
SGT300 8MW Industrial Gas Turbine Multi-Pass Cooled First Stage Rotor Blade
Nov 2010
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HP Turbine Blade Coatings Hot Gas Surface Coatings for Corrosion & Oxidation protection Aluminide, Silicon Aluminide (Sermalloy J) Chromising Chrome Aluminide, Platinum Aluminide MCrAlY Internal Coatings on Cooled Blades operating in poor environments
Ceramic Thermal Barrier Coatings Yttria stabilised Zirconia Plasma Spray Coatings used on Vanes EBPVD Coatings used on rotating blades More uniform structure for improved integrity
Page 46
Nov 2010
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Turbine Validation Process Analysis
Design
Assess evaluation and calibration of methods
Prototype
Test
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Nov 2010
Page 47
New technology incorporated into existing engine platforms SGT-100 Product Development New ratings have been released
Compressor Blade • Stator stages S1& S2 • Rotor stages R1 & R2
Aerodynamic modifications to compressor and turbine. HP Rotor blade • SX4 material • Triple fin shroud • Step Tip seal
Power generation, 5.4MWe (launch rating 3.9MW previously 5.25MWe)
Mechanical Drive,
5.7MW
(previously 4.9MW)
T
Page 48
P
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Industrial Gas Turbines Advanced Materials & Manufacturing
SGT400 PT 2 Nozzle Ring Page 49
Nov 2010
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Bladed Turbine Disc
Page 50
Nov 2010
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The Gas Turbine Package In addition to the main package, the following is also required: Combustion air intake system Gas turbine exhaust system Enclosure ventilation system (if enclosure fitted) Control system UPS or battery and charger system
Page 51
Nov 2010
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SGT-300 Industrial gas turbine Package design – The latest Module Design Available as a factory assembled packaged power plant for utility and industrial power generation applications Easily transported, installed and maintained at site Package incorporates gas turbine, gearbox, generator and all systems mounted on a single underbase Preferred option to mount controls on package, option for off package. Common modular package design concept Acoustic treatment to reduce noise levels to 85 dB(A) as standard (lower levels available as options) Page 52
Nov 2010
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Typical Compressor Set
Page 53
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Nov 2010
SGT-400 New Package Design Minimised customer interfaces reducing contract execution/installation costs 1 1
Combustion Air Intake
2
Enclosure Air Inlet
3
On-Skid Controls
4
Fire & Gas System
5
Interfaces
6
Lub Oil Cooler
7
Enclosure Air Exit
7
6
2 3
4 5
Highly flexible modular construction Customer configurable solutions based upon pre-engineered options Standard module interfaces to allow flexibility and inter-changeability Additional functionality provided dependent upon client needs Base design provides common platform for on-shore and off-shore PG and MD Page 54
Nov 2010
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Future direction
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Future Trends - guided by market requirements Universal demand for further increases in efficiency and reliability, and reduction in cost. Oil & Gas (Mech drive and Power Gen) Fuel flexibility - associated gases, off-gases, sour gas Remote operation Emissions -inc CO2 Independent Power Generation Fuel flexibility - syngas, biofuels(?), LPG Flexible operation - part load operation Distributed cogeneration (rather than centralised generation) Emissions - inc CO2
Page 56
Nov 2010
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Oil and Gas remote operations / fuel flexibility •First application of its kind in Russia (Western Siberia) burning wellhead gas which was previously flared •Solution: Three SGT-200 gas turbine •Output 6.75 MWe each •DLE Combustion system •Guaranteed NOx and CO emission levels of 25ppm •Min. air temp. (-57oC) •Max. air temp. (+34oC) •Gas composition with Wobbe Index >45MJ/m3 •Total DLE hours approximately 22,300 hours for each unit •Significant reduction of emissions : 80-90% reduction of NOx level •Siemens has supplied 135 gas turbines for Power Generation , Gas compression and pumping duty throughout the Russian oil & gas industry Page 57
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Nov 2010
Power Generation re-emergence of cogeneration WATER
GRID
FUEL
BOILER OR DRIER
PRODUCT / STEAM
~ Page 58
Nov 2010
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Thank You
Page 59
Nov 2010
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