Download - Hydro power plants
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Hydro power plants
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Hydro power plants
Tail water
Draft tube gate
Draft tube
TurbineMain valve
Penstock
Air inletInlet gate
Surge shaft
TunnelSand trap
Trash rack
Self closing valve
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The principle the water conduits of a traditional high head power plant
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Ulla- Førre
Original figur ved Statkraft Vestlandsverkene
![Page 5: Hydro power plants](https://reader033.vdocuments.us/reader033/viewer/2022061607/56812c0e550346895d907d49/html5/thumbnails/5.jpg)
Intake gate
Intake trashrack
Headrace tunnel
Anchor block
Surge tank
Penstock inletValve
Tunnel Inlettrashrack
Tunnel Inlet
Anchor block
Exp. joint
Shaddle
Power house
TailraceIV G
SC
DTR
DT end gate
Desilting basin
gate hoist
IV -inlet valveR -turbine runnerSC -spiral caseG -generator
Typical Power House with Francis Turbine
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Arrangement of a small hydropower plant
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H = 39 mQ = 513 m3/sP = 182 MWDrunner=7,5 m
Ligga Power Plant, Norrbotten, Sweden
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Borcha Power Plant, Turkey
H = 87,5 mP = 150 MWDrunner=5,5 m
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Water intake
• Dam• Coarse trash rack• Intake gate • Sediment settling basement
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Dams• Rockfill dams
• Pilar og platedammer
• Hvelvdammer
![Page 11: Hydro power plants](https://reader033.vdocuments.us/reader033/viewer/2022061607/56812c0e550346895d907d49/html5/thumbnails/11.jpg)
Rock-fill dams
1. Core Moraine, crushed soft rock, concrete, asphalt2. Filter zone Sandy gravel3. Transition zone Fine blasted rock4. Supporting shell Blasted rock
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Slab concrete dam
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Arc dam
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Gates in Hydro Power Plants
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Types of Gates
• Radial Gates
• Wheel Gates
• Slide Gates
• Flap Gates
• Rubber Gates
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Radial Gates at Älvkarleby, Sweden
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Radial Gate
The forces acting on the arc will be transferred to the bearing
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Slide Gate
Jhimruk Power Plant, Nepal
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Flap Gate
![Page 20: Hydro power plants](https://reader033.vdocuments.us/reader033/viewer/2022061607/56812c0e550346895d907d49/html5/thumbnails/20.jpg)
Rubber gate
Reinforced rubberOpen position
Flow disturbance
Reinforced rubberClosed position Bracket
Air inlet
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Circular gate
ManholeHinge
Ladder
RibsPipe
End cover
Bolt
Fastening element
Frame Seal
![Page 22: Hydro power plants](https://reader033.vdocuments.us/reader033/viewer/2022061607/56812c0e550346895d907d49/html5/thumbnails/22.jpg)
Circular gate
Jhimruk Power Plant, Nepal
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Trash Racks
Panauti Power Plant, Nepal
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Theun Hinboun Power PlantLaos
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GravfossPower PlantNorway
Trash Rack size:Width: 12 meterHeight: 13 meter
Stainless Steel
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CompRack Trash Rack delivered by VA-Tech
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Cleaning the trash rack
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Pipes• Materials• Calculation of the change of length due to the
change of the temperature• Calculation of the head loss• Calculation of maximum pressure
– Static pressure– Water hammer
• Calculation of the pipe thickness• Calculation of the economical correct diameter• Calculation of the forces acting on the anchors
![Page 29: Hydro power plants](https://reader033.vdocuments.us/reader033/viewer/2022061607/56812c0e550346895d907d49/html5/thumbnails/29.jpg)
Materials
• Steel
• Polyethylene, PE
• Glass-fibre reinforced Unsaturated Polyesterplastic , GUP
• Wood
• Concrete
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MaterialsMaterial Max.
DiameterMax.
PressureMax.
Stresses
[m] [m] [MPa]
Steel, St.37 150
Steel, St.42 190
Steel, St.52 206
PE ~ 1,0 160 5
GUP 2,4Max. p = 160 m.
320Max. D: 1,4 m.
Wood ~5 80
Concrete ~5 ~ 400
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Steel pipes in penstockNore Power Plant, Norway
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GUP-PipeRaubergfossen Power Plant, Norway
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Wood Pipes
Breivikbotn Power Plant, Norway Øvre Porsa Power Plant, Norway
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Calculation of the change of length due to the change of the temperature
LTL Where:L = Change of length [m]
L = Length [m] = Coefficient of thermal expansion [m/oC m]T = Change of temperature [oC]
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Calculation of the head loss
g2
c
D
Lfh
2
f
Where:hf = Head loss [m]f = Friction factor [ - ]L = Length of pipe [m]D = Diameter of the pipe [m]
c = Water velocity [m/s]g = Gravity [m/s2]
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ExampleCalculation of the head loss
Dc
Re
Power Plant data:H = 100 m HeadQ = 10 m3/s Flow Rate
L = 1000 m Length of pipeD = 2,0 m Diameter of the pipeThe pipe material is steel
Where:c = 3,2 m/s Water velocity = 1,308·10-6 m2/s Kinetic viscosityRe = 4,9 ·106 Reynolds number
g2
c
D
Lfh
2
f
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0,013
Where:Re = 4,9 ·106 Reynolds number = 0,045 mm RoughnessD = 2,0 m Diameter of the pipe/D = 2,25 ·10-5 Relative roughness
f = 0,013 Friction factorThe pipe material is steel
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ExampleCalculation of the head loss
Power Plant data:H = 100 m HeadQ = 10 m3/s Flow Rate
L = 1000 m Length of pipeD = 2,0 m Diameter of the pipeThe pipe material is steel
Where:f = 0,013 Friction factorc = 3,2 m/s Water velocityg = 9,82 m/s2 Gravity
m4,382,92
2,3
2
1000013,0
g2
c
D
Lfh
22
f
![Page 40: Hydro power plants](https://reader033.vdocuments.us/reader033/viewer/2022061607/56812c0e550346895d907d49/html5/thumbnails/40.jpg)
Calculation of maximum pressure
• Static head, Hgr (Gross Head)
• Water hammer, hwh
• Deflection between pipe supports
• Friction in the axial direction
Hg
r
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Maximum pressure rise due to the Water Hammer
c
g
cah max
wh
hwh = Pressure rise due to water hammer [mWC]a = Speed of sound in the penstock [m/s]cmax = maximum velocity [m/s]
g = gravity [m/s2]
Jowkowskya
L2TIF C
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Example Jowkowsky
c=10 m/s
m1020g
cah max
wh
a = 1000 [m/s]cmax = 10 [m/s]
g = 9,81 [m/s2]
a
L2TC
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Maximum pressure rise due to the Water Hammer
C
max
C
maxwh Tg
L2c
Ta
L2
g
cah
Where:hwh = Pressure rise due to water hammer [mWC]a = Speed of sound in the penstock [m/s]cmax = maximum velocity [m/s]
g = gravity [m/s2]L = Length [m]TC = Time to close the main valve or guide vanes [s]
L
C
a
L2TIF C
![Page 44: Hydro power plants](https://reader033.vdocuments.us/reader033/viewer/2022061607/56812c0e550346895d907d49/html5/thumbnails/44.jpg)
Example
m61Tg
L2ch
C
maxwh
L = 300 [m]TC = 10 [s]cmax = 10 [m/s]
g = 9,81 [m/s2]
L
C=10 m/s
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Calculation of the pipe thickness
t
Crp
tL2CpDL
sit
tsi
whgr hHgp Where:
L = Length of the pipe [m]Di = Inner diameter of the pipe [m]p = Pressure inside the pipe [Pa]t = Stresses in the pipe material [Pa]t = Thickness of the pipe [m]Cs = Coefficient of safety [ - ] = Density of the water [kg/m3]Hgr = Gross Head [m]hwh = Pressure rise due to water hammer [m]
ri
t
pt t
• Based on:– Material properties – Pressure from:
• Water hammer• Static head
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ExampleCalculation of the pipe thickness
m009,0Crp
t
tL2CpDL
t
si
tsi
MPa57,1hHgp whgr
Where:L = 0,001 m Length of the pipeDi = 2,0 m Inner diameter of the pipet = 206 MPa Stresses in the pipe material = 1000 kg/m3 Density of the waterCs = 1,2 Coefficient of safetyHgr = 100 m Gross Headhwh = 61 m Pressure rise due to water hammer
ri
t
pt t
• Based on:– Material properties – Pressure from:
• Water hammer• Static head
![Page 47: Hydro power plants](https://reader033.vdocuments.us/reader033/viewer/2022061607/56812c0e550346895d907d49/html5/thumbnails/47.jpg)
Calculation of the economical correct diameter of the pipe
Diameter [m]
Cos
t [$]
Installation costs, Kt
Costs for hydraulic losses, Kf
Total costs, K tot
0
dD
KKd
dD
dK tftot
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ExampleCalculation of the economical correct diameter of the pipe
Hydraulic Losses
Where:PLoss = Loss of power due to the head loss [W] = Density of the water [kg/m3]g = gravity [m/s2]Q = Flow rate [m3/s]hf = Head loss [m]f = Friction factor [ - ]L = Length of pipe [m]r = Radius of the pipe [m]C2 = Calculation coefficient
52
42
2
fLoss r
C
rg2
Q
r2
LfQghQgP
Power Plant data:H = 100 m HeadQ = 10 m3/s Flow Rateplant = 85 % Plant efficiency
L = 1000 m Length of pipe
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ExampleCalculation of the economical correct diameter of the pipe
Cost of the Hydraulic Losses per year
Where:Kf = Cost for the hydraulic losses [€]PLoss = Loss of power due to the head loss [W]T = Energy production time [h/year]kWhprice = Energy price [€/kWh]r = Radius of the pipe [m]C2 = Calculation coefficient
price52
priceLossf kWhTr
CkWhTPK
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ExampleCalculation of the economical correct diameter of the pipe
Present value of the Hydraulic Losses per year
price52
f kWhTr
CK
Where:Kf = Cost for the hydraulic losses [€]T = Energy production time [h/year]kWhprice = Energy price [€/kWh]r = Radius of the pipe [m]C2 = Calculation coefficient
Present value for 20 year of operation:
n
1ii
fpvf
I1
KK
Where:Kf pv = Present value of the hydraulic losses [€]n = Lifetime, (Number of year ) [-]I = Interest rate [-]
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ExampleCalculation of the economical correct diameter of the pipe
Cost for the Pipe Material
21mmm rCL
rpr2Ltr2Vm
Where:m = Mass of the pipe [kg]
m = Density of the material [kg/m3]V = Volume of material [m3]r = Radius of pipe [m]L = Length of pipe [m]p = Pressure in the pipe [MPa]
= Maximum stress [MPa]C1 = Calculation coefficientKt = Installation costs [€]M = Cost for the material [€/kg]
21t rCMmMK
NB:This is a simplification because no other component then the pipe is calculated
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ExampleCalculation of the economical correct diameter of the pipe
• Installation Costs:– Pipes– Maintenance– Interests– Etc.
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ExampleCalculation of the economical correct diameter of the pipe
21t rCMK
Where:Kf = Cost for the hydraulic losses [€]Kt = Installation costs [€]T = Energy production time [h/year]kWhprice = Energy price [€/kWh]r = Radius of the pipe [m]C1 = Calculation coefficientC2 = Calculation coefficientM = Cost for the material [€/kg]n = Lifetime, (Number of year ) [-]I = Interest rate [-]
n
1ii
price52
pvfI1
kWhTrC
K
0I1
kWhTC
r
5rCM2
dr
KKd n
1ii
price2
6ft
![Page 54: Hydro power plants](https://reader033.vdocuments.us/reader033/viewer/2022061607/56812c0e550346895d907d49/html5/thumbnails/54.jpg)
ExampleCalculation of the economical correct diameter of the pipe
7
n
1ii
price2
n
1ii
price2
6ft
I1CM
kWhTC
2
5r
0I1
kWhTC
r
5rCM2
dr
KKd
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Calculation of the forces acting on the anchors
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Calculation of the forces acting on the anchors
F5
F4F3
F1
F2
F
F1 = Force due to the water pressure [N]F2 = Force due to the water pressure [N]F3 = Friction force due to the pillars upstream the anchor [N]F4 = Friction force due to the expansion joint upstream the anchor [N]F5 = Friction force due to the expansion joint downstream the anchor [N]
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Calculation of the forces acting on the anchors
G
F
R
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Valves
![Page 59: Hydro power plants](https://reader033.vdocuments.us/reader033/viewer/2022061607/56812c0e550346895d907d49/html5/thumbnails/59.jpg)
Principle drawings of valvesOpen positionClosed position
Spherical valve Gate valve
Hollow-jet valve Butterfly valve
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Spherical valve
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Bypass system
![Page 62: Hydro power plants](https://reader033.vdocuments.us/reader033/viewer/2022061607/56812c0e550346895d907d49/html5/thumbnails/62.jpg)
Butterfly valve
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Butterfly valve
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Butterfly valvedisk types
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Hollow-jet Valve
![Page 66: Hydro power plants](https://reader033.vdocuments.us/reader033/viewer/2022061607/56812c0e550346895d907d49/html5/thumbnails/66.jpg)
Pelton turbines
• Large heads (from 100 meter to 1800 meter)
• Relatively small flow rate
• Maximum of 6 nozzles
• Good efficiency over a vide range
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Kværner
Jostedal, Norway
*Q = 28,5 m3/s*H = 1130 m*P = 288 MW
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Francis turbines
• Heads between 15 and 700 meter
• Medium Flow Rates• Good efficiency
=0.96 for modern machines
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SVARTISEN
P = 350 MWH = 543 mQ* = 71,5 m3/SD0 = 4,86 mD1 = 4,31mD2 = 2,35 mB0 = 0,28 mn = 333 rpm
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Kaplan turbines
• Low head (from 70 meter and down to 5 meter)
• Large flow rates • The runner vanes can
be governed • Good efficiency over
a vide range
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