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J. Energy Power Sources Vol. 1, No. 2, 2014, pp. 72-78 Received: July 1, 2014, Published: August 30, 2014
Journal of Energy and Power Sources
www.ethanpublishing.com
Towards an Innovative Radial Flow Impulse Turbine and
a New Horizontal Archimedean Hydropower Screw
Bernhard Mayrhofer1, Alkistis Stergiopoulou2, Bernhard Pelikan1 and Efrossini Kalkani2
1. Department of Water, Atmosphere and Environment, University of Natural Resources and Life Sciences, Institute for Water
Management, Hydrology and Hydraulic Engineering, Vienna, 1190, Austria
2. Department of Water Resources and Environmental Engineering, National Technical University of Athens, School of Civil
Engineering, Athens, 15780, Greece
Corresponding author: Alkistis Stergiopoulou ([email protected])
Abstract: The present paper explores the performance characteristics of two innovating hydropower systems, a radial flow impulse turbine and a new horizontal Archimedean screw system. Concerning the radial flow impulse turbine a functional description with a theoretical analysis of the turbine principle is given and the results of the first hydraulic measurements of a 7.5 kW prototype are shown. The analysis shows that the turbine efficiency is with 36.6 % low, in comparison to other turbines. In terms of the horizontal Archimedean screw the principle idea and a preliminary theoretical calculation of the screw are given. The preliminary theoretical calculation indicates an efficiency of 22 %. To verify the calculated efficiency a practical experiment arrangement is planned and described in this paper. Key words: Small hydropower, radial impulse turbines, Archimedean screw turbines, kinetic energy.
1. Introduction
All turbines convert hydraulic energy into rotational
mechanical energy, which is subsequently converted in
electric energy. There are three types of turbines, the
reaction, the impulse and the Archimedean screw
turbines, the difference being mainly the manner of
water head conversion. In the reaction turbines, the
fluid fills the blade passages, and the head change or
pressure drop occurs within the runner. An impulse
turbine first converts the water head through a nozzle
into a high-velocity jet, which then strikes the buckets
at one position as they pass by. The runner passages are
not fully filled, and the jet flow past the buckets is
essentially at constant pressure. Impulse turbines are
ideally suited for high head and relatively low power
[1].The third type of hydropower turbine concerns the
low and zero head Archimedean screw systems with
inclined and horizontal axis efficient and technically
feasible machines.
In the last centuries many turbines, which work on
the basis of the three types, have been invented. This
doesn’t mean that there can’t be new inventions in this
field. The paper presents experimental research of an
IRFIT (Innovative Radial Flow Impulse Turbine) and
preliminary research efforts for a HAAHT (Horizontal
Axis Archimedean Hydropower Turbines) harnessing
the kinetic energy of rivers, currents and open channels
works.
2. Functional Description of the IRFIT
Fig. 1 shows a schematical picture of the researched
IRFIT and of its 8-bladed rotor [2]. The supplied water,
which is under pressure, comes from the bottom and
flows through a reduction to the jet nozzle. The jet
nozzle converts the energy of the water stream into
kinetic energy and deflects the water into the radial
direction. The water jet passes centrifugally the rotor,
Towards an Innovative Radial Flow Impulse Turbine and a New Horizontal Archimedean Hydropower Screw
73
where rotor blades deflect the water. The deflection
leads to a momentum, which moves the rotor and
causes a torque. The energy from the rotor is led by a
shaft to the generator. The rotor and the shaft are fixed
with a bearing. This bearing absorbs all the forces and
contains the sealing, which prevents flow out of the
housing. After having passed the rotor the housing
collects the water and brings it back to the river channel.
It also contains the mounting of the turbine.
The housing is not completely filled with water, so
that the rotor is surrounded by air, which results in
lower friction losses and ensures atmospheric pressure
conditions. This also allows air to enter the rotor
through an air gap which is the most important
characteristic of the turbine, as explained later. Due to
the air there is no force locked connection between
upstream and downstream water, which results in head
losses.
Fig. 2 shows the cylinders used for the flow rate
regulation of the radial impulse turbine. With these
cylinders it is possible to lift and lower the rotor. This
leads to a change of the jet nozzle gap, which is among
Fig. 1 Turbine description.
Fig. 2 IRFIT regulation.
other factors responsible for the flow rate. After the air
gap the jet nozzle is necessary, because all the available
potential energy should be converted into kinetic
energy. The air also ensures that there is almost no
retroactivity from the rotor to the jet nozzle. In the rotor
channel the air should reduce the friction losses,
because of the resulting higher hydraulic diameter and
is necessary for the flow rate regulation.
For this turbine a high relative output velocity is
important. The air allows a maximum speed of the
water jet because it reduces the water filled
cross-section area, so that theoretically by a lower flow
rate more air is in the channel, the water filled
cross-section area decrease and according to the
equation of continuity the velocity of the water jet
remains constant. The ambient air pressure around and
inside the rotor, the radial jet inlet flow and the loading
principle differentiate the researched turbine from
other types, such as Francis as well as Pelton turbines.
3. A First Theoretical Analysis of IRFIT
With the theoretical analyses the maximum
efficiency of the researched turbine should be
determined. This research is based on an ideal turbine
without losses. This ideal turbine has an endless
number of rotor blades with a thickness of zero. The
water jet enters the rotor inlet normal to the
circumferential direction and leaves the rotor outlet
tangential against the circumferential direction. No air
in the rotor is considered. By using this assumption and
the law of conservation of energy, the ideal turbine
efficiency ηideal can be determined, as Eq. (1) shows:
ηideal=1- P2
P1=1- m·c2
2
2
m·c12
2
=1- c22
c12 (1)
P1 and P2 represent the input and output power of the
water jet, the mass flow and c1 and c2 the input and
output velocity of the water jet [3-4]. The input velocity
is a function of the head H and the gravitational
acceleration g, as written in Eq. (2):
c1= 2·g·H (2)
The output velocity can be calculated with the relative
74
Fig. 3 Theore
water velocit
circumferenti
Both veloc
(4)-(5), wher
rotation speed
Fig. 3 il
depending on
The diag
circumferenti
maximal effi
calculations o
that with the
velocity also
rotation speed
low heads a
efficiency, be
can be relati
practically th
The theore
principle is si
same behavio
turbine effici
[5-6]. Howev
significant co
nozzle of the
that a flow re
4. IRFIT M
To determ
efficiency a p
T
etical maximum
ty at the roto
ial velocity u2
c2=cities w2 and u
re r represents
d:
w2=u2=
llustrates the
n the outlet cir
gram shows
ial velocity an
iciency of the
of a turbine w
e increase of
the friction lo
d exists. This
are not neces
ecause with lo
ively higher
e turbine has
etical analysis
imilar to the S
or according t
iency under
ver, the resear
onstruction d
new turbine i
egulation can b
Measuremen
mine the Rad
prototype has b
Towards an InHoriz
m turbine effici
or outlet w2
2, see Eq. (3): w2+u2
u2 can be calcu
s the rotor ra
2·g·H+u22
r·2·π·n
e ideal turbi
rcumferential
s, that a
nd a low head
e idealized tu
with friction
f the outlet c
osses rise, so t
s calculation a
ssarily positiv
ow heads the
than with h
an optimal he
s also shows t
Segner Wheel
to the theoret
the mentione
rched turbine
details. For ex
is located befo
be realized.
nts
dial Flow Im
been built and
novative Radzontal Archim
iency.
and the outle
(3ulated with Eq
adius and n th
(4
(5
ine efficienc
velocity.
high outle
d increases th
urbine. Simpl
losses indicat
circumferentia
that an optima
also shows tha
ve for a hig
friction losse
high heads. S
ead.
that the turbin
, which has th
tical maximum
ed assumptio
features som
xample the je
ore the rotor s
mpulse Turbin
tested on a te
ial Flow Impumedean Hydro
et
3)
qs.
he
4)
5)
cy
et
he
le
te
al
al
at
gh
es
So
ne
he
m
on
me
et
so
ne
st
Fig. 4 dimensi
Fig. 5
rig. Th
and a d
power
heads
operati
with th
The
speed,
efficien
efficien
3.8 bar
It sh
occurs
is lowe
short d
small
rotation
by arou
is repr
rotation
measur
ulse Turbine apower Screw
Radial Flow Iions.
Efficiency dep
he prototype ha
discharge of 2
is around 7.5
and dischar
ional rage of t
he main dimen
diagrams illu
the pressure
ncy. Fig. 5 pr
ncy and rotatio
r.
hows that the
by a rotation
er than the pl
deviation from
influence on
n speed reduc
und 1.3 %. Th
resented by th
nal speed is s
red efficiency
nd a New
Impulse Turbin
pending on the r
as been design
25.5 l/s, so tha
kW. For the
rge were us
the turbine. In
nsions is show
ustrate the infl
and the flow
resents the con
on speed by a
e highest effi
speed of app
lanned rotatio
m this optimal
n the efficien
ction of 20 % r
he influence o
he jet nozzle
mall. At the p
y the turbine h
ne Prototype w
rotation speed.
ned for a head
at the hydraul
measurement
sed to ident
n Fig. 4 the pr
wn.
fluence of the
w rate on the
nnection from
pressure from
iciency from
proximately 18
on speed of 2
l rotation spee
ncy. For exa
reduces the ef
of the flow rate
gap, on the
point with the
has a specific
with main
.
d of 30 m
lic input
ts higher
tify the
rototype
rotation
turbine
m turbine
m around
36.6 %
8 s-1 and
25 s-1. A
ed has a
ample a
fficiency
e, which
optimal
e highest
rotation
Fig. 6 Efficie
Fig. 7 Efficie
speed from a
depends also
each pressure
with best mea
of the chara
pressures high
In the third
function of th
This diagra
raises the tur
with a higher
too.
In genera
maximum me
commercial u
can change
considered in
and may be u
quantity of w
5. TowardHydropowe
The possi
energy of wat
T
ncy depending
ncy depending
approximately
on the pressu
e and jet noz
asured rotation
cteristic curv
her turbine ef
d diagram (see
he flow rate is
am shows that
rbine efficien
flow rate the
al the meas
easured turbin
usage and it is
this fact, if
n detail. Despit
used in devel
water.
ds Horizonter Turbines
ibility of ex
tercourses, hyd
Towards an InHoriz
on the pressur
on the flow rat
y 13 min-1. T
ure, as the Fig
zzle gap the o
n speed is show
ves indicates
fficiency could
e Fig. 7), the
s presented.
t an increase o
ncy. It further
turbine effici
surement sho
ne efficiency i
not likely tha
the theoretic
te the turbine
oping countri
tal Axis As (HAAHT)
xploiting kin
draulic networ
novative Radzontal Archim
re.
te.
The efficienc
g. 6 shows. Fo
operation poin
wn. The cours
that at highe
d be reached.
efficiency as
of the flow rat
r indicates tha
ency could ris
ows that th
is too low for
at optimization
al principle
is easy to buil
ies with a hig
Archimedea)
etic hydrauli
rks, marine an
ial Flow Impumedean Hydro
cy
or
nt
se
er
a
te
at
se
he
a
ns
is
ld
gh
an
ic
nd
Fig. 8
tidal cu
given l
large
exploit
techno
the new
installe
the Lab
Hydrol
the dim
(depth)
The
pitch S
L = 1 m
mm, n
rotor c
(Δθ =1
initial p
initial p
Som
rotation
Accord
horizon
The ro
“above
ulse Turbine apower Screw
Design of the h
urrents, for p
little attention
renewable en
ted by “
logies” [7-10]
w Horizontal A
ed and experim
boratory of th
logy and Hydr
mensions Lchan
) = 1 m, are gi
length L, the
S and the numb
m, Do = 200 m
= 3 (number
could rotated
100°), forming
position and a
position (see F
me information
n of the horizo
ding to the fir
ntal and is ba
otor could be
e” and “below
nd a New
horizontal screw
power generat
, although suc
nergy resour
“modern A
].The geometr
Archimedean
mented in the
he Institute for
raulic Enginee
nnel = 4.17 m, b
iven in Fig. 8
e diameters (o
ber of blades o
mm, Di = 100 m
r of blades). T
horizontally
g an upstream
a downstream
Fig. 9).
n concerning tw
ontal screw is g
rst possibility
sed on a “gui
moved along
w” (inside the h
w rotor.
tion, have bo
ch currents rep
rce which co
Archimedean
rical character
Screw Rotor
e hydraulic ch
r Water Mana
ering, in Vien
bchannel = 1.4 m
.
output and inp
of the screw ro
mm, S/Do = 1,
The horizonta
and change d
m angle of 50°
m angle of 50°
wo possibilitie
given in Fig. 1
the screw rot
ide” at his rig
g its “guide”
hydraulic chan
75
oth been
present a
ould be
screw
ristics of
recently
annel of
agement,
nna, with
m, hchannel
put), the
otor are:
S = 200
al screw
direction with its
with its
es for the
10 below.
tor stays
ght edge.
towards
nnel of a
Towards an Innovative Radial Flow Impulse Turbine and a New Horizontal Archimedean Hydropower Screw
76
Fig. 9 The horizontal screw rotor could change
horizontally direction (Δθ = 100°).
Fig. 10 Rotation possibilities of the horizontal screw.
Fig. 11 Artistic photorealistic view of a series of horizontal screw rotors in the natural channel of Euripus Strait.
Fig. 12 Views of the new 3-bladed horizontal axis Archimedean screw turbine.
depth 1 m). According to the second possibility the
horizontal screw rotor could be rotated horizontally (θ1,
θ2, θ3…) with the help of the “right guide”, which
could also be rotated.
An artistic photorealistic view of a series of
horizontal screw rotors in the natural channel of
Euripus Strait, Greece, is given below in Fig. 11.
Some views of the new 3-bladed horizontal axis
Archimedean screw turbine, before installing in the
experimental channel of the Laboratory are given in
Fig. 12.
6. Preliminary HAAHT Theoretical Efforts
To illustrate a quite simple basic theory of horizontal
screw machine based on the drag principle, the
classical undershot waterwheel with flat blades is
considered as a good example to simulate a horizontal
screw waterwheel. Consider the screw waterwheel,
having an effective radius R, a blade area Ab and an
angular velocity ω rotating in a stream flow of velocity
Vc (see Fig. 13).
The force exerted on the flat blade, simulating one
screw blade, is given by Eq. (6):
Fd=0.5·ρ·Ab·Cd· Vr2 (6)
where ρ represent the fluid density, Cd is the blade
coefficient of drag and Vr is the difference (Vc - Vb)
Towards an Innovative Radial Flow Impulse Turbine and a New Horizontal Archimedean Hydropower Screw
77
Fig.13 Screw waterwheel rotating in stream flow of velocity Vc = V.
between stream flow velocity Vc and blade velocity Vb
= ω * R. The relative velocity Vr decreases as ω/R
approaches V c and the force Fd decreases toward zero.
The power produced by the blade can be calculated
with Eq. (7) PT=Fd·Vb (7)
and combining the previous relations gives the power: PT= 0.5·ρ·Ab·Cd·ω·R· Vc-Vb
2
= 0.5·ρ·Ab·Cd·ω·R· 1-λ2·Vc
3 (8)
where λ is the tip-speed ratio. By using Eq. (9)
Cp=Cd·λ· 1-λ2 (9)
the power equation reduces to
PT=0.5·ρ·Ab·Cp·Vc3 (10)
The derived function for Cp gives a value of zero for
λ = 0 and λ = 1 and a maximum value of 0.148 for λ =
1/3. However, based on the total projected area of the
screw waterwheel, the maximum power coefficient is
about 0.06. The power for constant-speed operation is
proportional to (Cp/λ3) but as the stream velocity
increases the power continues to increase. Τhe flow
and the geometrical data are Vc = 1.76 m/s, Αb = blade
wet area = Lb * (Ro - Ri) = 1 m * 0.05 m = 0.05 m2, Lb =
length of the blade, Ro and Ri are the outlet and the inlet
radius of the blade.
The theoretical power of the input current in the
open channel could be:
Pth=0.5·ρ·Ab·Cd·Vc3=136.29 W (11)
The power produced by the horizontal screw wheel is PT=ω·T=2·π·n·T (12)
where ω is the angular velocity of the runner, T is the
torque acting on the turbine shaft, and N is the
rotational speed of the runner. The hydraulic efficiency
of the screw turbine is defined as the ratio between the
mechanical power developed by the turbine to the
available theoretical water power, as Eq. (13) shows:
ηhyd=Pt
Pth=0.22 (13)
For the above preliminary HAAHTcalculations, the
following characteristic values are used: Fd = 51.62 N,
ω = 7.882 r/s, T = Fd * R = 3.8175 Nm, Vb = Vc/3 =
0.5866 m/s.
7. Conclusions and Further Researches
This paper has explored the performance
characteristics of two very promising hydropower
systems, an innovative radial flow impulse turbine and
a new horizontal Archimedean hydropower screw
system.
The functional description of the radial flow impulse
turbine shows the innovative concept of the researched
turbine. Theoretically the turbine is similar to the
Segner Wheel, although the design and operating
principle show considerable differences. The
measurement results have shown that the efficiency of
the investigated prototype reaches only 36.6 %. The
measured data indicates that at higher pressures and
flow rates an increased efficiency can be obtained.
Without the maximum efficiency it is hard to analyses
the turbine performance, so that further measurements
with more operation points are necessary. Due to
optimizations, for example of the jet nozzle, the rotor,
the air gap and so on, the efficiency could be increased.
Therefore more measurements of different prototypes,
mathematic calculations or simulation are needed.
The preliminary theoretical calculation of the
horizontal Archimedean screw indicates an efficiency of
22 %. To verify this efficiency practical measurements
on the described experiment arrangement are necessary.
With these measurements also the optimal operation
condition for a high efficiency can be determined and
general advices for the use of horizontal Archimedean
screws can be given.
References
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Towards an Innovative Radial Flow Impulse Turbine and a New Horizontal Archimedean Hydropower Screw
78
[2] B. Mayrhofer, Untersuchung der Tellerstrahlturbine-Beschreibung des Funktionsprinzips, Wirkungsgradabschätzung und Analyse des Anwendungspotentials, FH Technikum Wien, Vienna, 2014.
[3] D.G. Shepherd, Principles of Turbomachinery, Macmillan, 1956.
[4] C.H. Wu, A General Theory of Two- and Three-Dimensional Rotational Flow in Turbomachines, NASA Contractor Report 4496, 1993.
[5] B.S. Leo, S.T. Husu, A simple reaction turbine as a solar engine, Solar Energy 2 (1958) 7-11.
[6] A.A. Date, Design and cost analysis of low head simply reaction hydro turbine for remote area power supply, Renewable Energy 34 (2009) 409-415.
[7] B. Pelikan, A. Lashofer, Verbesserung der Strömungseigenschaften sowie Planungs und Betriebsoptimierung von Wasserkraftschnecken Research Project, BOKU University, Vienna , 2012. (in German)
[8] P.J. Kantert, Praxishandbuch Schneckenpumpe, Hirthammer Verlag, 2008.
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