Institute of Optimi ed Integration of PostOptimized ... cap/4-2 sec.pdf · Concept study Reference...
Transcript of Institute of Optimi ed Integration of PostOptimized ... cap/4-2 sec.pdf · Concept study Reference...
Optimi ed Integration of PostOptimized Integration of Post-Combustion CO2 Capture Process i G fi ld P Pl t
Jochen Oexmann
Institute ofEnergy Systems
in Greenfield Power PlantsImo Pfaff
Sebastian Linnenberg
Alfons Kather
Hamburg University of TechnologyInstitute of Energy Systems
12th International Post Combustion Capture Network Meeting
30 September 2009, Regina, CanadaProf. Dr.-Ing. A. Kather
Hamburg University of TechnologyInstitute of Energy Systems
Background
Post-combustion CO2 capture by wet chemical absorption processes + Based on the conventional steam power plant process
R t fitt bl+ Retrofittable− Relatively high efficiency penalty
Effi i l d tOther CO2
Structure of efficiency losses
Efficiency losses due to ▸ CO2 capture unit
• Heat demand to regenerate solvent
compression
PowerHeat demand to regenerate solvent• Power demand
▸ CO2 compression Heat
▸ Further auxiliary loads (fans etc.) CO2 capture unit
Focus of most studies: Retrofit integration
This study: focus on GreenfieldW t t l d ll l t ti i ti ibl▸Water-steam-cycle and overall power plant optimization possible
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Hamburg University of TechnologyInstitute of Energy Systems
Methodology (1)
Reference power plant process (Ebsilon Professional)
▸ Concept study Reference Power Plant North Rhine-Westphalia (RPP-NRW)(USC, hard-coal, ηnet = 45.6 %, 600 MWel, gross )
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Hamburg University of TechnologyInstitute of Energy Systems
Methodology (1)
Reference power plant process (Ebsilon Professional)
▸ Concept study Reference Power Plant North Rhine-Westphalia (RPP-NRW)(USC, hard-coal, ηnet = 45.6 %, 600 MWel, gross )
Wet chemical absorption process (Aspen Plus)
▸MEA based process with optimistic performance parameters:
3.3 GJ/t CO2 @ 124 °C (90% capture)flue gas
from FGDto atmosphere make-up
waterfrom FGD
to CO2-storage
intercooled compression
washing section overhead
condenser
solvent cooler
water
rich-leanHX
desorberabsorber
to make-up water system
steam/condensatefrom/to
power plant
blower
solvent pump(CO2-rich)
reboiler
flue gas cooler solvent pump(CO2-lean)
l i
filter
4
to water conditioning or FGD
reclaimer
disposal
Hamburg University of TechnologyInstitute of Energy Systems
Methodology (1)
Reference power plant process (Ebsilon Professional)
▸ Concept study Reference Power Plant North Rhine-Westphalia (RPP-NRW)(USC, hard-coal, ηnet = 45.6 %, 600 MWel, gross )
Wet chemical absorption process (Aspen Plus)
▸MEA based process with optimistic performance parameters:
3.3 GJ/t CO2 @ 124 °C (90% capture)
CO2 compression process (Ebsilon Professional)
▸ 8-staged compressor, each stage intercooled
▸ Pipeline conditions 110 bar, 40 °C
1 2 3/4 6/75 8
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Hamburg University of TechnologyInstitute of Energy Systems
Methodology (2)
M
M
MM
CO2 Capture UnitSteamCondens ate Power Cool outCool in
Fl ue gas
TG
CO2
CCR
Compressor1 2
345
e l. Eig e n b ed a r fa u c h g a s r e in ig u n g
1 4 . 1 5 9 M Wa u g u n g a u s d e m Ke s s e lh a
0. 983 37 5. 000
39 9. 926 98 6. 553
0. 971 12 0. 046
12 3. 557 98 6. 553
0. 971 11 6. 691
11 9. 972 10 33. 71 2
45 36. 43 3 kW
1. 000 40 . 000
40 . 470 94 3. 192
1. 042 44 . 446
44 . 972 94 3. 192
1. 008 48 . 902
51 . 224 10 53. 49 3
1. 008 48 . 902
51 . 243 10 52. 56 2
1. 008 48 902
30 . 432 0 931
0. 960 11 6. 857
12 0. 436 10 21. 90 4
17 8. 918 kW
1. 008 12 2. 988
12 6. 852 10 21. 90 4
13 683. 7 22 kW
1. 042 44 . 446
44 . 972 47 . 160
0.900
Flue gas side CO2 Capture and CO2 Compressor
M
MM
Qzu = 2295 .15 MW
Nettowirkungsgrad34.70 %
Klem m enleistung Nettoleistung
B ruttow irkungsgrad40.24 %
Eig e n b e d a rKe s s e l
3 . 9 1 1 M W
284. 899 600. 000
3461. 134 824. 090
274. 999 596. 416
3459. 403 824. 090
923519.342 kW
58. 988 620. 000
3706. 533 690. 830
796479.474 kW 3. 937 238. 856
2941. 868 264. 428
57. 998 618. 890
3704. 680 690. 830
2. 850 kg/ s 2900. 000 kJ/ kg
1. 061 kg/ s
0. 902 kg/ s 3. 937 238. 856
2941. 868 265. 330
1. 913 235. 100
2941. 643 131. 174
97. 959 186. 625
796. 720 4. 120
1. 913 235. 100
2941. 643 129. 765
2 1 8 7 1 9 3 . 5 0 4 k W
9 1 . 8 0 6 k g / s 4 4 . 2 2 1 ° C
0. 995 37 5. 000
39 9. 926 98 6. 553
1. 000 33 9. 021
34 9. 261 75 8. 323
1. 000 50 0. 000
65 2. 637 1. 285
22 95. 14 8 kW
23 70. 87 4 kW
48 . 902 0. 931 1. 012 25 . 000
10 4. 929 31 . 589
70 04. 06 7 kW
29 6. 559 kW
3. 000 25 . 000
30 . 987 91 . 806
0. 960 11 6. 857
94 . 975 11 . 809
Get aG 0. 989
e t a i0 . 9 2 0
P7 0 . 7M W
e t a i0 . 9 2 0
P8 5 . 7M W
e t a i0 . 9 2 0
P8 2 . 8M W
et a i0 . 9 1 0
P71 . 1
P - I P S T
4 7 8 . 5 M W
T 5 2 . 0
1 0 0 M
T 2 0 . 0
1 9 2 M
P - H P S T
3 2 3 . 7 M W
e t a i0 . 9 2 0
P8 2 . 8M W
e t a i0 . 9 2 0
P8 5 . 7M W
e t a i0 . 9 2 0
P7 0 . 7M W
e t a i0 . 8 0 1
P7 . 3
M W
e t a i0 . 8 1 0
P1 1 . 6M W
e t a i0 . 8 0 9
P5 . 6
M W
P - L P S T
6 5 . 1 M W
e t a i0 . 8 0 9
P5 . 6
M W
e t a i0 . 8 1 0
P1 1 . 6M W
e t a i0 . 8 0 1
P7 . 3
M W
e t a i0 . 7 7 6
P8 . 0
M W
El . Ei genbedarf13 .76 %
e t a i0 . 8 0 0
P7 . 2
M W
e t a i0 . 8 0 9
P6 . 4
M W
e t a i0 . 8 0 9
P1 1 . 3M W
P - L P S T
? ? ? M W
e t a i0 . 8 0 9
P1 1 . 3M W
e t a i0 . 8 0 9
P6 . 4
M W
e t a i0 . 8 0 0
P7 . 2
M W
e t a i0 . 7 7 3
P8 . 5
M W
e t a i0 . 7 7 6
P8 . 0
M W
et a i0 . 7 7 3
P8. 5
M W
DT 2. 3 K
61. 998 356. 968
3058. 528 686. 710
319. 899 306. 875
1362. 866 824. 090
60. 988 355. 527
3056. 998 686. 710
88. 282 410. 082
3151. 380 54. 913
27. 947 502. 353
3464. 591 46. 973
1 270 39 .868 k W
322. 186 °C 351. 668 °C
299. 667 °C
91. 012 411. 941
3151. 380 54. 913
3. 937 2941. 868
28. 812 502. 778
3464. 591 46. 973
91. 012 411. 941
3151. 380 54. 913 302. 157 °C
28. 812 502. 778
3464. 591 46. 973 0. 031
24. 873 0. 941
2401. 882 56. 695 2328. 574
1. 013 24. 115
22. 634 14731. 939
0. 028 22. 771 0. 937
2389. 486 56. 037 2584. 206
0. 031 24. 873 0. 941
2401. 882 56. 695 2328. 574
0. 028 22. 771 0. 937
2389. 486 56. 037 2584. 206
306. 875 °C 306. 875 °C
1. 176 190. 107
2855. 049 6. 400
0. 681 145. 025
2769. 142 9. 124
0. 000 kg/ s
KA
T 5 . 0 K
6 5 M
T 5 1 . 5
7 1 M
T 5 . 0 K
2 8 7 M
Q 257. 1 MW
Mühlenluf t abwärme
Nebenkühlwasser
Q 88. 6 MW
DT 2. 3 K
DT 2. 3 K
Q 98. 7 MW
Q 29. 4 MW
Q 14. 4 MWDT 2. 2 KDT 1. 3 K
Q 259. 5 MW
Mühlenluf t -WÜ
11. 570 370. 194
3198. 170 91. 367
3. 788 238. 590 1. 000
2941. 868 21. 830 13. 415
1. 153 189. 614 1. 000
2854. 186 7. 302 13. 436
301. 967 °C 277. 026 °C
321. 899 275. 313
1206. 910 797. 223 280. 314 °C
229. 411 °C
275. 736 °C
273. 435 °C
324. 249 227. 159
985. 713 797. 223
60. 137 355. 309
3058. 528 79. 402
238. 856 21. 830
232. 160 °C
0. 116 48. 777 0. 980
2541. 461 9. 472 118. 232
61. 998 356. 968
3058. 528 79. 402
11. 570 370. 194
3198. 170 88. 927
0. 028 22. 771
95. 517 112. 075
1. 013 20. 000
84. 013 264. 976
1. 013 11. 300
11. 416 14535. 058
0. 031 20. 000
83. 921 2. 777
23. 535 °C
0. 028 22. 771 0. 937
2389. 486 112. 075
1. 013 17. 714
74. 446 24170. 000
2. 481 28. 631
120. 243 2082. 000
0 044 2367 310
68. 095 kg/ s
0. 318 90. 072 1. 000
2665. 410 10. 477 55. 011
17. 729 °C
1. 270 kg/ s
0. 000 kg/ s
0. 663 144. 956 1. 000
2769. 142 9. 124 26. 391
61. 998 356. 968
3058. 528 0. 000
0. 031 24. 873 0. 941
2401. 882 113. 390
? ?
? ?
6750. 689 kW
T 5 . 0 K
2 7 7 M
1 5 . 63 7 . 4
K W S di 6 E ON E i i G bH
DT 1. 2 K0 . 7
? ? ? M W B re n s to f fwä rm e l e i s tu n g :
e rz e u g t e El e k t ro e n e rg i e (b ru2 3 .5 2 M W e rz e u g t e El e k t ro e n e rg i e (n e9 6 .4 8 M W a u s g e k o p p e l te F e rn wä rm e l e ? ? ? M W
Profi l : CCSrf_90
Q 19. 0 MW
DT 2. 9 K
Q 48. 4 MW
DT 1. 1 K
Q 24. 9 MW
DT 0. 7 K
Q 22. 1 MW
Q
Q 94. 8 MW
DT 1. 2 K1 . 7
Q 21. 9 MW
229. 411 C 198. 967 °C
141. 659 °C
176. 235 °C
11. 216 184. 935
785. 038 828. 210
184. 935 °C
29. 123 °C
574. 882 kW
14. 541 87. 357
366. 939 299. 648
14. 315 102. 568
430. 925 328. 779
14. 020 140. 806
593. 327 328. 779 28. 457 °C
15. 300 25. 957
110. 248 280. 046 69. 307 °C
P bar T °C X -
H kJ/kg M kg/s VM m³/s
319. 949 191. 024
827. 232 26. 867
11. 288 369. 952
3198. 170 42. 332
0. 044 30. 555 0. 922
2367. 310 42. 332 1245. 534
3 4 8 2 0 .3 6
0. 031 24. 873
108. 298 280. 046
0. 044 30. 555 0. 922
2367. 310 42. 332 1245. 534
326. 529 190. 944
827. 232 824. 090
48. 060 °C
30. 555 °C 42. 332 kg/ s
59. 668 kW
45. 551 kW
K W Staudinger 6
080923_SK_Ref erenz_CCS
E. ON Engineer ing G mbH EEN-TKP-Kul 25. 02. 2008 CCSr f _90
A n l a g e n wi rk u n g s g ra d (b ru t toA n l a g e n wi rk u n g s g ra d c a . (n ? ? ? %
? ? ? %
A n l a g e n n u t z u n g s g ra d (b ru t tA n l a g e n n u t z u n g s g ra d c a . (n
? ? ? %? ? ? %
Abdampf quer schnit t 4 x 14 m² Um gebungsluf t t emperat ur 11. 3°C
• Integration of CO2 capture unit by implementing interface characteristics in
Water-steam-side
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“yellow-box” within power plant simulation tool EBSILONProfessional
Hamburg University of TechnologyInstitute of Energy Systems
Methodology (2)
• Integration of CO2 capture unit by implementing interface characteristics in
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“yellow-box” within power plant simulation tool EBSILONProfessional
Hamburg University of TechnologyInstitute of Energy Systems
Study Approach
CCS power plant
▸ Design point: 100 % load with 90 % CO2 capture
▸ Flow sheet layout unchanged to maintain comparability
For each design case
▸Optimization of steam bleed pressures of pre-heat train
▸Optimal reboiler condensate return point
Conducted analyses
1. Evaluate impact IP/LP crossover pipe pressure (basic integration)
2. Optimization by waste heat recovery
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Hamburg University of TechnologyInstitute of Energy Systems
Basic Integration
Interface requirements delivered by the power plant
1. Heat for regeneration in sufficient quantity and quality
2. Power to drive the CO2 compressor, pumps and fans
3. Cooling water to discharge waste heat
Only reasonable option to extract LP-steam: IP/LP crossover pipe
▸ Best suited to extract large steam quantity (~ 50% needed)
▸ To meet the required quality (T,p) over entire load range
• steam attemperationreboilersuperheated spraysuperheated
steamfrom IP/LP
crossover pipe
p yattemperator
zo condensatepre-heat train
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Hamburg University of TechnologyInstitute of Energy Systems
Basic Integration
Interface requirements delivered by the power plant
1. Heat for regeneration in sufficient quantity and quality
2. Power to drive the CO2 compressor, pumps and fans
3. Cooling water to discharge waste heat
Only reasonable option to extract LP-steam: IP/LP crossover pipe
▸ Best suited to extract large steam quantity (~ 50% needed)
▸ To meet the required quality (T,p) over entire load range
• steam attemperation 3.3 bar t CCU• pressure maintenance concept:
Treboiler + ΔT = 124 + 10 = 134 °Csteam @ 3 0 bar + 8 % press
to CCU
IP/ LPsteam @ 3.0 bar + 8 % press.loss: 3.3 bar
IP/ LPcrossover pipe
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Hamburg University of TechnologyInstitute of Energy Systems
Impact of IP/LP Crossover Pipe Pressure
10035.9
% %
Choice of IP/LP design pressure:trade-off between design point and part-load efficiency
80
90
35.7
35.8
oint
in %
ressure
ation in %Part load in which
IP/LP pressure would dropbelow 3.3 bar in base case:
6 4 %
50
60
70
35 4
35.5
35.6
design
po
itho
ut pr
e in ope
ra56.4 %
30
40
50
35.2
35.3
35.4
ency
atd
l loa
d wi
nce valce
0
10
20
34 9
35.0
35.1
Net effici
Minim
aainten
anNet efficiency decreasein base case:- 10.6 %-pts.
034.9
3.3 3.5 3.7 3.9 4.1 4.3 4.5 4.7 4.9 5.1 5.3 5.5
IP/LP crossover pipe design pressure in bar
N ma
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IP/LP crossover pipe design pressure in barbase case
Hamburg University of TechnologyInstitute of Energy Systems
Optimisation by Waste Heat Recovery (I)
Potential sources of waste heat for recovery
▸ Reasonable temperature level needed
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Hamburg University of TechnologyInstitute of Energy Systems
Optimisation by Waste Heat Recovery (I)
Possible heat sinks for direct integration combustion air
pre heatingpre-heating
condensate pre-heating
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Hamburg University of TechnologyInstitute of Energy Systems
Optimisation by Waste Heat Recovery (I)
Potential sources of waste heat for recovery
▸ Reasonable temperature level needed
• Desorber overhead condenser (OHC)
• Intercoolers and aftercooler of CO2 compressor
Possible heat sinks for direct integration
▸ Condensate pre-heating
▸ Combustion air pre-heating
Advanced heat integration improve temperature level of the waste heat
▸ Skipping distinct intercoolers of CO2 compressor (heat pumping)
▸ Advanced combustion air pre-heat configuration (heat shifting)
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Hamburg University of TechnologyInstitute of Energy Systems
C b i
Advanced Combustion Air Pre-Heat Configuration
Combustionair
APH
4 5
4
5
Flue gas
APHSec I
Fl
3
ure
T6
3
4 6
7APHSec II
Ai h t
Flue gastemperature
> Tdew2 Te
mpe
ratu
7 2
3
Air heater (bleed steamfrom turbines) APH Sec I APH Sec II
TransferredHeat Q
1
T 1
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Hamburg University of TechnologyInstitute of Energy Systems
C b i
Advanced Combustion Air Pre-Heat Configuration
Combustionair
APH
4 5
4
5
Flue gas
APHSec I
Fl
3
ure
T6
3
4 6
7APHSec II
Ai h t
Flue gastemperature
> Tdew2 Te
mpe
ratu
7 2
3
(waste heatfrom OHC orintercoolers)
Air heater
APH Sec I APH Sec II
TransferredHeat Q
1
TWaste heat input
1
intercoolers)
i. Waste heat replaces steam bleed air heater (ηnet +0.3 %-pts.)
p
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Hamburg University of TechnologyInstitute of Energy Systems
C b i
Advanced Combustion Air Pre-Heat Configuration
Combustionair
APH
4 5
4
5
Flue gas
APHSec I
Fl
3
ure
T6
3
4 6
7APHSec II
Ai h t
Flue gastemperature
> Tdew2 Te
mpe
ratu
7 2
3
(waste heatfrom OHC orintercoolers)
Air heater
APH Sec I APH Sec II
TransferredHeat Q
1
TWaste heat input
1
intercoolers)
i. Waste heat replaces steam bleed air heater (ηnet +0.3 %-pts.)
ii. Increased waste heat integration leads to higher flue gas losses
p
g g g
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Hamburg University of TechnologyInstitute of Energy Systems
C b i
Advanced Combustion Air Pre-Heat Configuration
Combustionair
APH
4 5
4
5
Flue gas
APHSec I
BypassFl
3
ure
T6
3
4 6
7APHSec II
Ai h t
ypeconomiser
(HP feedwater heater)
Flue gastemperature
> Tdew2 Te
mpe
ratu
7 2
3
(waste heatfrom OHC orintercoolers)
Air heater
APH Sec I APH Sec II
TransferredHeat Q
1
TWaste heat input
1
intercoolers)
i. Waste heat replaces steam bleed air heater (ηnet +0.3 %-pts.)
ii. Increased waste heat integration leads to higher flue gas losses
p
g g g
iii. Bypass economiser to decrease flue gas outlet temperature (+0.5 %-pts. total)
i. High costs of additional gas-liquid heat exchanger
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i. High costs of additional gas liquid heat exchanger
ii. Lower temperature difference in APH ▸ larger HX area ▸ larger costs
Hamburg University of TechnologyInstitute of Energy Systems
Optimisation by Waste Heat Recovery (II)
-0,1 0 0,1 0,2 0,3 0,4 0,5 0,6 0,7 0,8 0,9No Heat recovery measure
Efficiency improvement in % points
OHC-Condensate
OHC APH
eat eco e y easu e
1 OHC ► Condensate
2 OHC ► Combustion Air Si l h tOHC-APH
IC8_T55
2 OHC ► Combustion Air
3 7 IC ► Condensate
Simple heatrecovery
IC4_T40
IC2_T40
4 3 IC ► Condensate
5 1 IC ► Condensate Advancedheat recovery
OHC+Adv. APH6 OHC ► Advanced APH
7 Combination of 1+5Combinations
8 Combination of 1+5+6Combinations
19
Hamburg University of TechnologyInstitute of Energy Systems
Conclusions
Heat demand predominant reason for efficiency penalty
Design point and part-load efficiency strongly depend on IP/LP pressure
▸ Careful consideration of scheduled power plant operation
• Excess of 2.2 bar decreases efficiency by 0.9 % points at design point
• Slope of part-load efficiency improved with increased crossover pipe pressure
Optimization by waste heat recovery
▸ Up to 0.9 % points advancement in overall net efficiency
▸ Increases degree of integration potentially lowers availability / operability
▸Most cost effective option has to be evaluated
20
Hamburg University of TechnologyInstitute of Energy Systems
Thank you for your attention!
Institute of Energy SystemsJochen Oexmann - [email protected]
Institute of Energy Systems
This work has been submitted for publication in “Energy”.