U.S. patent application number 13/591881 was filed with the patent office on 2013-05-09 for driving engine (water turbine) of hydrokinetic floating power plant with enhanced efficiency degree, and hydrokinetic floating power plant module.
The applicant listed for this patent is Ivan Korac. Invention is credited to Ivan Korac.
Application Number | 20130115045 13/591881 |
Document ID | / |
Family ID | 42985701 |
Filed Date | 2013-05-09 |
United States Patent
Application |
20130115045 |
Kind Code |
A1 |
Korac; Ivan |
May 9, 2013 |
Driving Engine (Water Turbine) Of Hydrokinetic Floating Power Plant
With Enhanced Efficiency Degree, And Hydrokinetic Floating Power
Plant Module
Abstract
Improvements in hydrokinetic floating power plant efficiency are
obtained by optimization of (1) gaps z and z' between the
hydrokinetic driving engine blades and internal sidewalls and floor
of the working channel of the driving engine; (2) the ratio of the
submerged part of blade height in liquid and part of blade height
above the liquid surface; (3) the angles of inlet side planes and
bottom planes of a confusor and the outlet side planes of the
diffusor; and (4) distance t between blades and number n
simultaneously submerged blades in the working channel of the
driving engine.
Inventors: |
Korac; Ivan; (Zagreb,
HR) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
Korac; Ivan |
Zagreb |
|
HR |
|
|
Family ID: |
42985701 |
Appl. No.: |
13/591881 |
Filed: |
August 22, 2012 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
|
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PCT/HR2010/000004 |
Feb 22, 2010 |
|
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13591881 |
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Current U.S.
Class: |
415/8 |
Current CPC
Class: |
F03B 17/064 20130101;
B63H 1/02 20130101; Y02E 10/20 20130101; Y02E 10/28 20130101 |
Class at
Publication: |
415/8 |
International
Class: |
B63H 1/02 20060101
B63H001/02 |
Claims
1. A hydrokinetic driving engine, comprising: a working channel
defined by bounded by two sidewalls and an floor and having cross
sectional area A; two parallel endless chains holding a plurality
of blades, said blades being moved into and out of the working
channel with the blades located in the working channel maintained
perpendicular to a direction of water flow in the working channel;
the blades having side edges and a bottom edge; the blade side
edges and the working channel internal sidewalls being separated by
a gap z; the blade bottom edge and the working channel internal
floor being separated by a gap z'; the blades being separated from
each other by a distance t; a confusor having inlet side planes and
an inlet bottom plane located at an inlet of the working channel,
and having an inlet cross section surface A0; a diffusor having
outlet side surfaces located at an outlet of working channel having
an outlet cross section surface B0 gear assemblies which convert
linear movement of the plurality of blades in the working channel
to rotary movement of a gear shaft; an electrical generator
operably connected to the gear shaft, wherein: a ratio of an
un-submerged part of blade height to a submerged part of blade
height with respect to an outside water line prior to water inflow
into the confusor is 10 to 25%; an inclination angle .alpha. of
confusor side planes relative to the working channel sidewalls is
20.degree. to 30.degree.; an inclination angle .gamma. of a
confusor bottom plane with respect to working channel floor is
10.degree. to 30.degree.; an inclination angle .beta. of diffusor
outlet side surfaces relative to the working channel sidewalls is
10.degree. to 20.degree., gaps z and z' are 2-10% of a blade
surface, a number n of simultaneously entirely submerged blades in
the working channel is 2-6, and distance t between adjacent blades
is 0.5-3.0 m.
2. A hydrokinetic driving engine according to claim 1, wherein a
ratio A0/A of confusor inlet cross section A0 and working channel
cross section A is 2 to 4.
3. A hydrokinetic driving engine according to claim 2, wherein the
ratio A0/A of confusor (10) inlet cross section surface A0 and
working channel cross section A is 4.
4. A hydrokinetic driving engine according to claim 1, wherein a
ratio of diffusor outlet cross section surface B0 and working
channel cross section A is 2 to 4.
5. A hydrokinetic driving engine according to claim 4, wherein the
ratio of diffusor outlet cross section surface B0 and working
channel cross section A is 4.
6. A hydrokinetic driving engine according to claim 1, wherein the
size of gaps z and z' is 10% of the blade surface.
7. A hydrokinetic driving engine according to claim 1, wherein the
distance t between adjacent blades is 3.0 m.
8. A hydrokinetic floating power plant module, comprising: a
floating power plant platform connected to four anchor blocks and
four buoys; a hydrokinetic driving engine, including: a working
channel defined by bounded by two sidewalls and an floor and having
cross sectional area A; two parallel endless chains holding a
plurality of blades, said blades being moved into and out of the
working channel with the blades located in the working channel
maintained perpendicular to a direction of water flow in the
working channel; the blades having side edges and a bottom edge;
the blade side edges and the working channel internal sidewalls
being separated by a gap z; the blade bottom edge and the working
channel internal floor being separated by a gap z'; the blades
being separated from each other by a distance t; a confusor having
inlet side planes and an inlet bottom plane located at an inlet of
the working channel, and having an inlet cross section surface A0;
a diffusor having outlet side surfaces located at an outlet of
working channel having an outlet cross section surface B0 gear
assemblies which convert linear movement of the plurality of blades
in the working channel to rotary movement of a gear shaft; an
electrical generator operably connected to the gear shaft, wherein:
a ratio of an un-submerged part of blade height to a submerged part
of blade height with respect to an outside water line prior to
water inflow into the confusor is 10 to 25%; an inclination angle
.alpha. of confusor side planes relative to the working channel
sidewalls is 20.degree. to 30.degree.; an inclination angle .gamma.
of a confusor bottom plane with respect to working channel floor is
10.degree. to 30.degree. an inclination angle .beta. of diffusor
outlet side surfaces relative to the working channel sidewalls is
10.degree. to 20.degree., gaps z and z' are 2-10% of a blade
surface, a number n of simultaneously entirely submerged blades in
the working channel is 2-6, and distance t between adjacent blades
is 0.5-3.0 m; and a casing enclosing the hydrokinetic driving
engine.
9. A hydrokinetic floating power plant module according to claim 8,
wherein a ratio A0/A of confusor inlet cross section A0 and working
channel cross section A is 2 to 4.
10. A hydrokinetic floating power plant module according to claim
9, wherein the ratio A0/A of confusor (10) inlet cross section
surface A0 and working channel cross section A is 4.
11. A hydrokinetic floating power plant module according to claim
8, wherein a ratio of diffusor outlet cross section surface B0 and
working channel cross section A is 2 to 4.
12. A hydrokinetic floating power plant module according to claim
11, wherein the ratio of diffusor outlet cross section surface B0
and working channel cross section A is 4.
13. A hydrokinetic floating power plant module according to claim
8, wherein the size of gaps z and z' is 10% of the blade
surface.
14. A hydrokinetic floating power plant module according to claim
8, wherein the distance t between adjacent blades is 3.0 m.
Description
CROSS-REFERENCE TO RELATED APPLICATIONS
[0001] The present Application is a continuation of pending
International Patent Application PCT/HR2010/000004 filed on Feb.
22, 2010, which designates the United States, and the content of
which is incorporated herein by reference.
FIELD OF THE INVENTION
[0002] The present invention is a hydrokinetic engine for a
hydrokinetic floating power plant with enhanced efficiency, and a
hydrokinetic floating power plant module for electric power
generation, which uses the kinetic energy of river water flow. In
particular, the invention relates to a water engine with improved
individual element parameters that provide increased water flow
efficiency in the water engine working channel improved power
generation output of the hydrokinetic floating power plant
module.
[0003] The invention is referred to technical field which is
according to International patent classification (IPC) designated
under No. FO3B9/00 and refers to driving engines for liquids driven
by endless chain.
BACKGROUND OF THE INVENTION
[0004] All known technical solutions in the field of kinetic energy
usage of hydrodynamic flow of fluids recover only a portion of the
moving fluid's energy. Heretofore, no effective solutions have been
proposed which would increase the efficiency of energy recovery in
a hydrokinetic engine.
[0005] Since the existing technical solutions have typically
exhibited low efficiency, such systems have not been widely used
since they lack the needed commercial cost effectiveness.
[0006] DE102007003323A1 discloses a device with multiple blades
submerged in water. The blade's plane is perpendicular to water
flow direction. The blades are connected by means of a wheel
parallel to flow. Blades are fixed to transmission device which
transfer longitudinal movement of blades to rotating generator
shaft.
[0007] FR2532364 discloses a hydroelectric power plants using water
power as source of energy where force is acting in direction of
rotation of the half of blades and not perpendicular as it is with
most of hydroelectric power plants. A hydroelectric power plant is
located at the most suitable location where water is flowing with a
sufficient stream for electric power generation and without having
impact on fish migration and requirements for larger intervention.
The device can be completely manufactured in a factory. It includes
two buoys (f) and (g) interconnected by plate (h) and contains
protective grid. Between buoys are placed movable blades which are
maintained perpendicular to flow direction by means of pre-stressed
calibrated springs (b) and by which the force acting upon blades is
controlled. Blades are fixed to two driving chains (c) and by
virtue of shafts cause rotation of two kinetic wheels, gears and
alternator.
[0008] DE202006013818U1 discloses a floating conveyer unit with
blades driving the electric power generator.
[0009] WO2009103131A2 discloses an electric power plant producing
hydroelectric power. The power plant contains a pontoon (3) with
confusor (5) and diffusor (7) which are connected through working
channel (6) where generators (8) are mounted within the confusor
and diffusor. Along the working channel (6) and on the pontoon are
placed transmission systems (4) which shafts are connected with
power generator (9). Big (12) and small (13) sprockets/wheels are
connected with transmission system shafts (16) of transmission
system (4), which drive long (14) and short (15) sprockets/belts
where are long (19) and short (20) parts connected to long (14) and
short (15) sprockets/belts respectively on which are placed groups
of blades (18) where each individual blade (21) is at defined angle
relative to working channel (6) axis. Pontoon (3) is kept at fixed
location by means of anchors (2).
[0010] No single prior art reference mentioned above solves the
technical problem of increasing efficiency, but only disclose
general construction characteristics of hydroelectric power plants,
and do not disclose solutions based on optimizing the efficiency of
individual elements.
SUMMARY OF THE INVENTION
[0011] The present invention relates to the enhancement of
efficiency degree of hydrokinetic floating power plant module by
defining individual parameters of the driving engine of the
hydrokinetic floating power plant.
[0012] By the present invention, an increased efficiency in the use
of water flow kinetic energy is provided by improving the
hydrokinetic engine working channel and optimizing the gaps z and
z' between blades and driving engine working channel planes, the
number n referring to number of submerged blades in driving engine
working channel, mutual distance between blades, part of the blade
height submersed in liquid vs. part of blade height above water
surface ratio, as well as the dimensions of the confusor and
diffusor. The present invention provides an increase of efficiency
in a hydrokinetic floating power plant module.
[0013] The following details and parameters of the improved
hydrokinetic driving engine of the present invention provide a
significantly improved efficiency in converting the elements
contributing to improvement of efficiency in converting water flow
kinetic energy into power by improving the hydrokinetic engine
working channel: [0014] 1. determination of optimal gap between
blades and internal planes of driving engine channel which is
necessary, that with sufficient water and blade velocity in the
channel, the wanted water level difference in front and behind
blade is achieved and corresponding force on the blade is
accomplished. [0015] 2. determination of optimal relation between
blade height submerged in liquid and part of blade height above
liquid level with respect to the external liquid level prior to
inflow into confusor. [0016] 3. determination of dimensions and
form of confusor and diffusor, and [0017] 4. determination of
distance between blades and number of submerged blades in driving
engine channel by which a more constant force of liquid acting on
blades is accomplished.
BRIEF DESCRIPTION OF THE DRAWINGS
[0018] Below is given a short description of drawings and detailed
description of invention along with analysis of impact that have a
distance between adjacent blades, gap size between blades and
internal planes of driving engine channel, dimensions and form of
confusor and diffusor and blade velocity.
[0019] Invention will be described in detail with reference to the
drawing where:
[0020] FIG. 1 shows a hydrokinetic floating power plant module;
[0021] FIG. 2 shows a driving engine assembly in perspective view
with sequence of interconnected blades by endless chain;
[0022] FIG. 3 shows a driving engine assembly in perspective view
with sequence of interconnected blades by endless chain;
[0023] FIG. 4 shows a driving engine assembly in perspective view
with sequence of interconnected blades by endless chain;
[0024] FIG. 5 shows a side view of driving engine assembly with
sequence of interconnected blades by endless chain;
[0025] FIG. 6 shows a schematic presentation of the driving engine
in side view;
[0026] FIG. 7 shows a schematic presentation of the driving engine
in plan view;
[0027] FIG. 8 shows a s diagram of force change during tested
periods for distance between blades being 0.8 m;
[0028] FIG. 9 shows a diagram of force change during tested periods
for distance between blades being 3.0;
[0029] FIG. 10 shows a diagram of force change during tested period
for distance between blades being 6.0 m;
[0030] FIG. 11 shows a diagram of force change on blades with 10%
gap between tunnel and blades in tunnel model with 10 blades being
at mutual distance 0.8 m;
[0031] FIG. 12 shows a diagram of force change on blades with 20%
gap between tunnel and blades in tunnel model with 10 blades being
at mutual distance 0.8 m;
[0032] FIG. 13 shows a diagram of force change on blades with 30%
gap between tunnel and blades in tunnel model with 10 blades being
at distance 0.8 m;
[0033] FIG. 14 shows a diagram of force change on blades in tunnel
model with 10 blades being at distance 0.8 m and with 10% gap
between tunnel and blades at inclination of confusor 45.degree. and
diffusor 25.degree.;
[0034] FIG. 15 shows a diagram of force change on blades in tunnel
model with 10 blades being at distance 0.8 m and 10% gap between
tunnel and blades at inclination of confusor 20.degree. and
diffusor 20.degree.;
[0035] FIG. 16 shows a diagram of correlation power P(kW) vs.
velocity v (m/s) for diffusor and confusor inclination being
45.degree. and 25.degree. respectively.
DETAILED DESCRIPTION OF THE INVENTION
[0036] The details and parameters of the driving engine elements
which contribute to an improvement of the hydrokinetic driving
engine efficiency and the hydrokinetic floating power plant module
efficiency were determined by implementation of commercial CDF
(Computational Fluid Dynamics) software. A 2-D flow of a water
stream around and within the hydrokinetic floating power plant was
simulated in order to examine the influence of geometry and
position of the driving engine in the water stream in system
efficiency. The k-.epsilon. model of turbulence and two kinds of
flow were studied, particularly: [0037] non-stationary flow with
floating blades and given velocity, and [0038] stationary flow with
imposed given velocity at blade equal to blade velocity.
[0039] In all cases undisturbed water incoming velocity was given
and equals to 2 m/s. The following parameters were studied to
analyze their impact on efficiency: [0040] 1) distance t between
two adjacent blades being 0.8, 3.0 and 6.0 m; [0041] 2) gap size z
and z' between blades (6) and planes (15) and (16) of the working
channel (14) in cases when z and z' are 10, 20 and 30%; [0042] 3)
inclination of confusor and diffusor plane angles .alpha., .beta.
and .gamma.; [0043] 4) blade velocity 1, 2 and 3 m/s for
undisturbed flow velocity being 2 m/s; [0044] 5) confusor and
diffusor input and output surface ratio respectively, and working
channel cross -section surface ratio being 3:1 and 4:1.
[0045] A hydrokinetic floating power plant module is presented in
FIG. 1. Hydrokinetic floating power plant module (1) is anchored at
a predetermined location by means of four concrete blocks (3) which
are connected through four buoys (2) to a floating power plant
platform. The hydrokinetic floating power plant module driving
engine (13) is located within casing (4).
[0046] FIGS. 2 to 4 present perspective view of the hydrokinetic
driving engine (13) with a sequence of blades (6) interconnected by
an endless chain (7).
[0047] FIG. 5 shows a side view of a driving engine assembly with
sequence of blades (6) interconnected by endless chain (7). In the
driving engine (13) kinetic energy of water, by the quantity of
movement change, is converted into mechanical rotary energy. The
working wheel shaft is connected by means of gear assemblies with
generator (9) where mechanical rotary energy is converted in
electrical energy. In the working channel (14) of driving engine
(13) is installed a sequence of blades (6), where the blade plane
is perpendicular to water flow direction. In order to achieve
continuous movement of blades (6), they are interconnected by an
endless chain (7). On the front and back side of driving engine
(13) are fitted gear assemblies/working wheels which linear
movement of blades (6) in the channel (14) convert into rotary
movement, maintain continuous movement of blades (6) and direct the
blade (6) entering into water and coming out perpendicular related
to water flow in the working channel (14) of driving engine (13).
Blades (6) are attached to endless chain (7) and are can be
directed to permit vertical entry and exit of blades (6) in and out
of the water stream to enable entry and exit from the water stream
with an even energy input. To achieve a steady water force acting
upon blades (6) as much as possible, the ratio of non-submerged to
submerged parts of blade height in relation to the outside water
line before inflow into the confusor should be 10% to 20%.
Furthermore, in order to accomplish as much as possible stable
water force acting upon blades (6), the range of number n
simultaneously entirely submerged blades (6) in the channel (14) of
driving engine (13) equals 2-6. Gears/working wheels assemblies at
front and back side of driving engine (13) convert linear movement
of blades (6) in working channel (14) into rotary movement, and
kinetic energy taken over by front wheel shaft is converted into
mechanical energy carried over to generator rotor (9) which
generates electrical energy.
[0048] Working channel (14) of driving engine (13) is formed by two
internal side planes (15) and bottom plane (16). Confusor (10) is
located at the entry of working channel (14) by which river flow is
collected and directed into working channel (14) of driving engine
(13). The dimensions and form of confusor enables collection of
targeted quantity of water out from river flow and increase water
velocity in the driving engine channel when compared to the water
level in the free river flow. For this purpose, the cross section
surface of input confusor A.sub.0 is three times bigger than
cross-section surface A of the driving engine channel (the ratio of
confusor surface with respect to channel surface A.sub.0/A=3/1).
Confusor (10) is bounded by three planes, i.e. by two side planes
(17) and bottom plane (18). FIGS. 6 & 7 show angles .alpha. and
.gamma. under which confusor planes (17) and (18) are connected to
working channel (14). Working channel (14) is bounded by three
planes set under 90.degree. angle. Side planes (17) of confusor
(10) are set under angle .alpha. with respect to the plane of
internal side planes (15), while confusor bottom plane (18) is set
under angle .gamma. with respect to bottom plane (16) of the
working channel (14) (see FIGS. 5 & 6). The inclination angle
.alpha. of side planes (17) and angle .gamma. of confusor (10)
lower plane (18) enable collection of 40% more directed water flow
into working channel (14) than would otherwise be collected if
.alpha.=.gamma.=0. The effect of passing this quantity of water
through the driving engine working channel (14) is to raise the
water level in channel (14). FIG. 5 indicates rise of water flow
(level of internal water) with respect to the water flow level
before entering into confusor (10) (the level of outside
water).
[0049] At the outlet from driving engine working channel (14) is
located diffusor (11) which promotes accelerated water output from
channel (14) and rapidly equalizes increased height of water column
in the channel with height of water in the free flow. By this
effect of hydraulic jump is additionally enforced at the last blade
(6) in the channel (14), which from the linear movement goes into
circular movement, and goes out perpendicularly to water flow
direction in the channel. Diffusor (11) is also bounded by three
planes, i.e. by two side planes (19) and bottom plane (20). Side
plane (19) of diffusor (11) is set under angle .beta. with respect
to the plane of internal side planes (15) of the working channel
(14). FIG. 6 & 7 illustrate schematic presentation of the
driving engine in side view and top view showing values l, h, t, z
and z' where l means width of the working channel (14), h the
height of water level in the working channel (14), t is distance
between adjacent blades (6), z and z' is gap between internal
planes (15) & (16) of the working channel (14) and end edges of
blades (6). The gap z is expressed in %, and is defined as ratio
between channel width l and the part being between end edges of the
blades (6) and planes (15) of the working channel (14). The gap z'
is expressed in %, and is defined as ratio between the height of
water level h and the part being between end edge of the blades (6)
and bottom plane (16) of the working channel (14).
[0050] The impact of confusor and diffusor inclination has been
examined in a working channel model with 10 blades having distance
between them 0.8 m and gaps z and z' 10%.
[0051] The following cases have been tested: [0052] confusor angle
2.alpha.=45.degree., diffusor angle 2.beta.32 25.degree.-200 cycles
[0053] confusor angle 2.alpha.=20.degree. diffusor angle
2.beta.=20.degree.-200 cycles
[0054] From analysis of diagrams presented in FIG. 14 and 15 can be
seen that with smaller confusor and diffusor angle (20.degree.),
see FIG. 15, a greater force is accomplished than it would be the
case with bigger confusor and diffusor angles (45.degree. and
25.degree.), see. FIG. 14. Increased efficiency degree of the
driving engine (13) is achieved: [0055] for confusor side planes
(17) inclination with respect to the plane of working channel side
planes (15), angle .alpha. in range from 20.degree. to 30.degree.,
[0056] for confusor bottom plane (18) inclination with respect to
the working channel bottom plane (16), angle .gamma. in range from
10.degree. to 30.degree., and [0057] for diffusor side planes (19)
inclination with respect to the plane of working channel side
planes (15), angle .beta. in range from 10.degree. to
20.degree..
[0058] Apart from influence of plane inclinations .alpha., .gamma.
and .beta. of confusor (10) and diffusor (11) on the efficiency of
driving engine (13), the influence of ratio confusor inlet cross
section A0 and diffusor outlet cross section B0 and cross section A
of the working channel (14) has been analyzed. A variant with
confusor and diffusor having four times larger cross section A0 and
B0 respectively than cross section A of the working channel (14)
for various blade velocities has been examined. These results are
given in the table below where .gamma. denotes distance from
adjacent module, v.sub.lop is blade velocity and v.sub.in is
velocity of water flow.
TABLE-US-00001 B0/A or v.sub.in v.sub.lop A0/A F P F/m.sup.2
P/m.sup.2 Y [m] [m/s] [m/s] [--] Q [m3/s] [N] [W] [N] [kW] 27.04 1
2 3x 0.75 510.56 1021.13 340.38 0.68 5.5 2 2.66 4x 2.00 13419.89
35696.90 8946.59 23.80 5.5 2 1.33 4x 1.00 24856.19 33058.74
16570.79 22.04
[0059] The greatest power has been obtained in the case of 5.5 m
distance from the adjacent block, with confusor inlet cross section
A0 and diffusor outlet cross section B0 increase four times with
respect to the working channel (14) cross section A, at blade
velocity v.sub.lop=2.66 m/s and water velocity v.sub.in=2 m/s. This
case is presented in the table in bold. The ratio of confusor input
cross section A0 and working channel cross section A-A0/A, and
ratio of diffusor outlet cross section B0 and working channel cross
section A-B0/A , are within range 2 to 4.
[0060] FIGS. 6 & 7 illustrate schematic presentation of driving
engine in side view with values l, h, t, z, and z' where l is width
of working channel (14), h is height of water level in working
channel (14), t is distance between adjacent blades (6) and z and
z' are gaps between internal planes (15) and (16) of working
channel (14) and end edges of blades (6). Increased water velocity
and level in working channel, gaps z and z' between planes (15) and
(16) of working channel (14) and end edges of blades (6) as well as
decreased blade velocity in time of overtake of water kinetic
energy result in water column height difference before and after
the blade by which the effect of hydraulic jump occurs resulting
with increase of force upon the blade, i.e. increase in take over
power at blade. In the example of a tunnel with 10 blades, with
distance between them being 0.8 m, the influence of gap size z and
z' to the accomplished forces on all blades (6) have been examined.
FIGS. 11, 12 and 13 present diagrams of force changes on the blades
with gaps z and z' between working channel (14) and end edges of
blades (6) being 10%, 20% and 30%. The following cases have been
examined: [0061] gap z and z' 10%-200 cycles [0062] gap z and z'
20%-400 cycles [0063] gap z and z' 30%-400 cycles
[0064] From diagrams in FIGS. 11, 12 and 13 one can see that
greater forces have been realized with lower gap values z and z'.
The greatest force has been realized in case of 10% gap between
tunnel and end edges of blade (6). Accordingly, the gaps z and z'
by which have been realized greater forces are in the range from 2%
to 10% of the blade (6) surface.
[0065] Further on, the influence of distance t between two adjacent
blades has been analyzed. It was analyzed the working channel (14)
with one blade traveling down the stream at given velocity and
after certain time the blade suddenly raised while at the beginning
of tunnel in the same time occurred another blade. The following
cases have been examined: [0066] distance t between blades 0.8
m-600 cycles [0067] distance t between blades 3.0 m-200 cycles
[0068] distance t between blades 6.0 m-200 cycles
[0069] Diagrams on FIGS. 8, 9 and 10 present change of force during
testing cycles, where one cycle is travel time for one blade from
its occurrence at the tunnel inlet until it's rising, for distance
between blades 0.8 m, 3.0 m and 6.0 m.
[0070] It was needed 200 to 600 cycles to stabilize periodic
flow.
[0071] From diagrams in FIGS. 8, 9 and 10 can be seen how distance
between blades affects the force magnitude. With the distance being
8.8 m the realized force is between 40 and 50 kN, and it is
unstable. Unlike to previous case, with distance being 3 to 6 m the
realized force was about 58 kN and was stable within the whole
range. Though, with distance between blades being 6 m the realized
force was a little bit bigger, however from commercial stand point
such dimensions are not acceptable. Increased efficiency degree of
the driving engine (13) is accomplished for distance t between
blades in range from 0.5-3.0 m.
[0072] By analysis of the influence of blade velocity in example
with stationary flow, the exchanged energy between tunnel inlet and
outlet cross sections has been calculated. The water velocity at
the inlet in domain was 2 m/s, and confusor (10) and diffusor (11)
angles were 2.alpha.=45.degree. and 2.beta.=25.degree.. FIG. 16
indicates diagram of power P (kW) dependence on velocity v (m/s)
for diffusor (11) angles: 2.alpha.=45.degree. and
2.beta.=25.degree.. Examined were cases for: [0073] blade velocity
1 m/s [0074] blade velocity 2 m/s [0075] blade velocity 3 m/s
[0076] Analysis of power exchanged shows that the greatest power is
achieved with blade velocity being 2 m/s, which corresponds to
optimal velocity of 33% of undisturbed velocity through tunnel
(without blades), and which would be 6 m/s with three times larger
tunnel cross section, and which provides power optimization at the
given stream velocity.
[0077] Finally, for solution of technical problem how to increase
water flow kinetic energy efficiency degree in the working channel
(14) of driving engine assembly (13), and by this to increase
efficiency of the whole hydrokinetic floating power plant (1),
ranges of parameters of individual elements are the following:
TABLE-US-00002 gap between blades and working channel z i z' 2-10%
distance between blades t 0.5-3.0 m confusor angle .alpha.
20.degree.-30.degree. diffusor angle .beta. 10.degree.-20.degree.
reduction of confusor A0/A 2-4 widening of diffusor B.sub.o/A 2-4
number of blades in working channel n 2-6 confusor angle with
respect to horizontal line .gamma. 10.degree.-30.degree.
[0078] A hydrokinetic floating power plant (1) can be used together
with driving engine assembly (13) as integrated floating module
which can be individually or aggregately installed by anchoring in
free river streams and derivative canals. In this way electric
power is generated for end user by ecological acceptable source
which contributes to generation of electric power from renewable
sources. By this, so generated electric power contributes to
general energetic efficiency and reduction of greenhouse gases.
This type of floating module enables flora and fauna migration from
river habitation, and because all assemblies are of mechanical
type, there is no environment pollution.
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