design of geothermal power plants holistic approach...
TRANSCRIPT
ENGINE Final Conference
Vilnius, Lithuania
12-15 February 2008
Stephanie Frick, Ali Saadat, Stefan Kranz GeoForschungsZentrum Potsdam
DESIGN OF GEOTHERMAL POWER PLANTS
holistic approach considering auxiliary power
ENGINE Final Conference, 12-15 February 2008
� Power plants serve for net power production
� Net power = gross power - auxiliary power
� Auxiliary power
Introduction
conversion cycle
1
ENGINE Final Conference, 12-15 February 2008
source: http://www.erdwaerme-kraft.de/ source: http://www.refplus.com/
� Power plants serve for net power production
� Net power = gross power - auxiliary power
� Auxiliary power
Introduction
conversion cycle
cooling cycle
1
ENGINE Final Conference, 12-15 February 2008
� Power plants serve for net power production
� Net power = gross power - auxiliary power
� Auxiliary power
Introduction
conversion cycle
cooling cycle
thermal water cycle
1
ENGINE Final Conference, 12-15 February 2008
� Power plants serve for net power production
� Net power = gross power - auxiliary power
� Auxiliary power
� For geothermal power plants, a maximum net power
output can‘t be reached by maximising the gross power
� Geothermal power plant design needs a holistic approach
Introduction
conversion cycle
cooling cycle
thermal water cycle
1
ENGINE Final Conference, 12-15 February 2008
Overview
� Methodical approach to power plant design
� Gross power characteristics
� Auxiliary power characteristics
� Practical approach to power plant design
� Conclusions & Outlook
2
ENGINE Final Conference, 12-15 February 2008
Methodical approach
� site-specific reservoir characteristics and ambient
conditions(→ boundary conditions)
PI = II = 30 m3/(h MPa)
TTW = 150 °C ρTW = 1,147 kg/m3
cp = 3,5 kJ/(kg K) depth = 4.500 m
Ta = 20 °Cφa = 65 %
3
ENGINE Final Conference, 12-15 February 2008
Methodical approach
� site-specific reservoir
characteristics and ambient
conditions (→ boundary conditions)
� plant-specific parameters (→ component quality)
∆T = 5 K∆p = 0,1 bar
∆T = 5 K∆p = 0,1 bar
ηi = 0,75ηm = 0,95
η = 0,8
Isobutane
η = 0,6
∆T, ∆p, η, …
3
ENGINE Final Conference, 12-15 February 2008
� site-specific reservoir
characteristics and ambient
conditions (→ boundary conditions)
� plant-specific parameters
(→ component quality)
� design parameters:
condensation temp. TKond
injection temperature TTW,in
thermal water mass flow mTW
Methodical approach
TKond
TTW,inmTW
.
3
ENGINE Final Conference, 12-15 February 2008
� site-specific reservoir
characteristics and ambient
conditions (→ boundary conditions)
� plant-specific parameters
(→ component quality)
� design parameters:
condensation temp. TKond
injection temperature TTW,in
thermal water mass flow mTW
Methodical approach
TKond
TTW,inmTW
.
3
What influence have the
design parameters on
power plant performance?
ENGINE Final Conference, 12-15 February 2008
Methodical approach
TKond
TTW,inmTW
3
Exemplary power plant in the North German Basin:
TTW = 150 °C
PI = 30 m3/(h MPa)
...
other parameters see slide 13
ENGINE Final Conference, 12-15 February 2008
Gross power characteristics
4
0
1000
2000
3000
4000
20 40 60 80 100
thermal water mass flow in kg/s
gro
ss p
ow
er
in k
W...
T_cond=30 °C : T_TWin=60°C
T_cond=40 °C : T_TWin=80°C
Plant-specific parameters, reservoir and ambient conditions = const. (see slide 13)
ENGINE Final Conference, 12-15 February 2008
Gross power characteristics
gross power = ƒ (Tcond, TTW,in) • mTW
.
0
1000
2000
3000
4000
20 40 60 80 100
thermal water mass flow in kg/s
gro
ss p
ow
er
in k
W...
T_cond=30 °C : T_TWin=60°C
T_cond=40 °C : T_TWin=80°C
400
500
600
700
800
60 65 70 75 80
thermal water injection temperature in °C
T_cond=30 °C
T_cond=40 °C
thermal water mass flow 20 kg/s
Plant-specific parameters, reservoir and ambient conditions = const. (see slide 13)
4
ENGINE Final Conference, 12-15 February 2008
Auxiliary power characteristics
Conversion cycle
Plant-specific parameters, reservoir and ambient conditions = const. (see slide 13)
0
100
200
300
400
20 40 60 80 100
thermal water mass flow in kg/s
T_cond=30 °C : T_TWin=60°C
T_cond=40 °C : T_TWin=80°C
po
we
r d
em
an
d c
on
ve
rsio
n c
ycle
in
kW.
..
5
ENGINE Final Conference, 12-15 February 2008
Auxiliary power characteristics
Conversion cycle
Power demand conversion cycle = ƒ (Tcond, TTW,in) • mTW
.
0
100
200
300
400
20 40 60 80 100
thermal water mass flow in kg/s
T_cond=30 °C : T_TWin=60°C
T_cond=40 °C : T_TWin=80°C
po
we
r d
em
an
d c
on
ve
rsio
n c
ycle
in
kW.
..
20
40
60
80
60 65 70 75 80
thermal water injection temperature in °C
T_cond=30 °C
T_cond=40 °C
thermal water mass flow 20 kg/s
Plant-specific parameters, reservoir and ambient conditions = const. (see slide 13)
5
ENGINE Final Conference, 12-15 February 2008
Auxiliary power characteristics
Cooling cycle (wet cooling tower)
0
400
800
1200
1600
20 40 60 80 100
thermal water mass flow in kg/s
po
we
r d
em
an
d w
et co
olin
g in
kW
...
T_cond=30°C : T_TWin=60°C
T_cond=40°C : T_TWin=80°C
100
150
200
250
300
Plant-specific parameters, reservoir and ambient conditions = const. (see slide 13)
6
ENGINE Final Conference, 12-15 February 2008
Auxiliary power characteristics
Cooling cycle (wet cooling tower)
Power demand cooling cycle = ƒ (Tcond) • TTW,in • mTW
.
0
400
800
1200
1600
20 40 60 80 100
thermal water mass flow in kg/s
po
we
r d
em
an
d w
et co
olin
g in
kW
...
T_cond=30°C : T_TWin=60°C
T_cond=40°C : T_TWin=80°C
0
50
100
150
200
250
300
30 35 40 45
condensation temperature in °C
T_TWin=60°C
T_TWin=70°C
T_TWin=80°C
thermal water mass flow 20 kg/s
Plant-specific parameters, reservoir and ambient conditions = const. (see slide 13)
6
ENGINE Final Conference, 12-15 February 2008
Auxiliary power characteristics
Thermal water cycle
Power demand thermal water cycle = ƒ (mTW ).
Plant-specific parameters, reservoir and ambient conditions = const. (see slide 13)
7
0
1000
2000
3000
4000
20 40 60 80 100
themal water mass flow in kg/s
po
we
r d
em
an
d th
erm
al w
ate
r cycle
in
kW.
..
ENGINE Final Conference, 12-15 February 2008
Practical approach
site-specific reservoir and ambient conditions
plant-specificparameters
designparameters
power plant
design
net power output
gross power output
8
ENGINE Final Conference, 12-15 February 2008
Exemplary power plant design
TTW = 150 °C, PI = 30 m3/(h MPa), depthreservoir = 4,500 mreservoir conditions
1,8 MWgross power
maximum net power
(wet cooling)
30 °Ccondensation temp.
460 kWnet power
66 °Cth. water injection temp.
56 kg/sthermal water mass flow
maximum gross power
(wet cooling)
Plant-specific parameters, ambient conditions = const. (see slide 13) 9
site-specific reservoir and ambient conditions
plant-specifcparameters
designparameters
power plant
design
net power
outputmaximum
gross power
ENGINE Final Conference, 12-15 February 2008
Exemplary power plant design
TTW = 150 °C, PI = 30 m3/(h MPa), depthreservoir = 4,500 mreservoir conditions
1,3 MW1,8 MWgross power
600 kW
33 °C
71 °C
41 kg/s
maximum net power
(wet cooling)
30 °Ccondensation temp.
460 kWnet power
66 °Cth. water injection temp.
56 kg/sthermal water mass flow
maximum gross power
(wet cooling)
Plant-specific parameters, ambient conditions = const. (see slide 13) 9
site-specific reservoir and ambient conditions
plant-specifcparameters
designparameters
power plant
design
maximumnet power
gross power
output
ENGINE Final Conference, 12-15 February 2008
0
400
800
1200
1600
2000
0 200 400 600 800
net power in kW
gro
ss p
ow
er
in k
W…
.
Conclusions
► Choice of mTW, TTW,in and Tcond has a decisive impact
on power plant performance
► A maximum net power
output can‘t be reached by
maximising the gross power!
► Geothermal power plant
design needs a holisticapproach
maximum
gross power
maximum
net power
.
10
ENGINE Final Conference, 12-15 February 2008
Outlook
� Successful geothermal project development needs a
detailed and site-specific analysis
� Further technical constraints need to be considered
� Possible combination with other energy carriers to hybrid-
plants (…please have a look at the poster “The combined use of geothermal
and biomass for power generation - drawbacks and opportunities –“)
11
ENGINE Final Conference, 12-15 February 2008
turbine
feed pump
condensator
heat transfer
thermal water
waste heat
(Biogas CHP)
heat
recuperation
turbine
feed pump
condensatorheat transfer
thermal water
waste heat I (Biogas CHP)
heatrecuperation
waste heat II (Biogas CHP)
BMKW
ORC
Kalina I
Kalina II
A B A B C A B CAreference cases
0
200
400
600
800
1000
1200
1400
1600
1800
0
200
400
600
800
1000
1200
1400
1600
1800
Ele
ctr
ic p
ow
er
in k
W
The combined use of geothermal and biomass for power generation- drawbacks and opportunities -
Jan Wrobel a, Martin Kaltschmitt a,b
a Institute for Environmental Technology and EnergyEconomics, Hamburg University of Technology
b Institute for Energy and Environment
IUEIUEIUEIUEIUEIUEIUEIUE
ENGINE Final Conference poster session
ENGINE Final Conference, 12-15 February 2008
Outlook
� Successful geothermal project development needs a
detailed and site-specific analysis
� Further technical constraints need to be considered
� Possible combination with other energy carriers to hybrid-
plants (…please have a look at the poster “The combined use of geothermal
and biomass for power generation - drawbacks and opportunities –“)
� Non-technical aspects can be further limiting factors
� Successful geothermal development needs integrating, holistic planning tools
11
ENGINE Final Conference, 12-15 February 2008
Thank you very much for your attention!
Contact: Stephanie Frick
GeoForschungsZentrum Potsdam
Telegrafenberg
14473 Potsdam
e-mail: [email protected]
http://www.gfz-potsdam.de/pb52
12
ENGINE Final Conference, 12-15 February 2008
Plant-specific parameters & site-specifc conditions
thermal water temperature 150°Creservoir depth 4,500 mthermal water heat capacity 3,5 kJ/(kg K)thermal water density 1,147 kg/m3
productivity-/injectivity index 30 m3/(h MPa)
ambient temperature 20°Crelative humidity 60%
reservoir and ambient conditions
down-hole pump efficiency 60%misc. parameter see [Legarth, 2005]
thermal water
cycle
wet cooling:water-sided pressure losses 1 barair-sided pressure losses 0,002 barcooling range 6Kapproach 3Kcooling tower constant 0,8cooling pump efficiency 80%fan efficiency 80%dry cooling: air-sided pressure losses 0,002 barfan efficiency 80%
cooling cycle
turbine isentropic efficiency 75%turbine mechanical efficiency 95%heat exchanger temp. gradients 5Kheat exchanger pressure losses 0,1 barworking fluid Isobutane
conversion cycle
plant-specific parameters
13
ENGINE Final Conference, 12-15 February 2008
Exemplary run of power output against
thermal water injection temperature
50 60 70 80 90 100
thermal water injection temperature
conversion efficiency
transferred heat
power output
Power output = transferred heat x conversion efficiency
14
ENGINE Final Conference, 12-15 February 2008
Auxiliary power characteristics
Cooling cycle (dry condensation)
0
400
800
1200
1600
20 40 60 80 100
thermal water mass flow in kg/s
po
we
r d
em
an
d d
ry c
oo
lin
g in
kW
... T_cond=30°C : T_TWin=60°C
T_cond=30°C : T_TWin=80°C
T_cond=40°C : T_TWin=60°C
T_cond=40°C : T_TWin=80°C
0
50
100
150
200
250
300
30 35 40 45
condensation temperature in °C
T_TWin=60°C
T_TWin=70°C
T_TWin=80°C
thermal water mass flow 20 kg/s
air-sided pressure loss 0,002 bar;
fan efficiency 80 %
Plant-specific parameter, reservoir and ambient conditions = const. (see slide 13)
15
Power demand cooling cycle = ƒ (Tcond) • TTW,in • mTW
.
ENGINE Final Conference, 12-15 February 2008
Exemplary power plant design
TTW = 150 °C, PI = 30 m3/(h MPa), depthreservoir = 4,500 mreservoir conditions
485 kW
1,1 MW
36 °C
73 °C
37 kg/s
maximum
net power
(dry cooling)
100 kW
1,8 MW
30 °C
66 °C
56 kg/s
maximum
gross power
(dry cooling)
600 kW
1,3 MW
33 °C
71 °C
41 kg/s
maximum
net power
(wet cooling)
460 kW
1,8 MW
30 °C
66 °C
56 kg/s
maximum
gross power
(wet cooling)
gross power
condensation temp.
net power
th. water injection temp.
thermal water mass flow
16