NZ602725B - Condenser for axial flow exhaust type steam turbine and geothermal power plant having the same - Google Patents
Condenser for axial flow exhaust type steam turbine and geothermal power plant having the same Download PDFInfo
- Publication number
- NZ602725B NZ602725B NZ602725A NZ60272512A NZ602725B NZ 602725 B NZ602725 B NZ 602725B NZ 602725 A NZ602725 A NZ 602725A NZ 60272512 A NZ60272512 A NZ 60272512A NZ 602725 B NZ602725 B NZ 602725B
- Authority
- NZ
- New Zealand
- Prior art keywords
- water
- condenser
- cooling
- condenser unit
- steam turbine
- Prior art date
Links
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 92
- 238000001816 cooling Methods 0.000 claims abstract description 50
- 239000000498 cooling water Substances 0.000 claims abstract description 29
- 239000007921 spray Substances 0.000 claims abstract description 25
- 230000003068 static Effects 0.000 claims abstract description 13
- 125000000773 L-serino group Chemical group [H]OC(=O)[C@@]([H])(N([H])*)C([H])([H])O[H] 0.000 claims description 3
- 102100002249 MAML3 Human genes 0.000 claims 1
- 101700019980 MAML3 Proteins 0.000 claims 1
- 238000010276 construction Methods 0.000 abstract description 14
- 230000001939 inductive effect Effects 0.000 abstract description 6
- 241000196324 Embryophyta Species 0.000 description 16
- 238000009434 installation Methods 0.000 description 14
- 238000009412 basement excavation Methods 0.000 description 11
- 230000000694 effects Effects 0.000 description 4
- 230000001965 increased Effects 0.000 description 4
- 150000002500 ions Chemical class 0.000 description 3
- RECVMTHOQWMYFX-UHFFFAOYSA-N oxygen(1+) dihydride Chemical compound [OH2+] RECVMTHOQWMYFX-UHFFFAOYSA-N 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 230000001105 regulatory Effects 0.000 description 2
- 230000000630 rising Effects 0.000 description 2
- 235000007575 Calluna vulgaris Nutrition 0.000 description 1
- 241000353097 Molva molva Species 0.000 description 1
- 239000008186 active pharmaceutical agent Substances 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 230000003247 decreasing Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000006011 modification reaction Methods 0.000 description 1
- 238000005191 phase separation Methods 0.000 description 1
- 238000004326 stimulated echo acquisition mode for imaging Methods 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01D—SEPARATION
- B01D5/00—Condensation of vapours; Recovering volatile solvents by condensation
- B01D5/0027—Condensation of vapours; Recovering volatile solvents by condensation by direct contact between vapours or gases and the cooling medium
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01D—SEPARATION
- B01D5/00—Condensation of vapours; Recovering volatile solvents by condensation
- B01D5/0078—Condensation of vapours; Recovering volatile solvents by condensation characterised by auxiliary systems or arrangements
- B01D5/009—Collecting, removing and/or treatment of the condensate
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K9/00—Plants characterised by condensers arranged or modified to co-operate with the engines
- F01K9/003—Plants characterised by condensers arranged or modified to co-operate with the engines condenser cooling circuits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24T—GEOTHERMAL COLLECTORS; GEOTHERMAL SYSTEMS
- F24T10/00—Geothermal collectors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B11/00—Controlling arrangements with features specially adapted for condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B3/00—Condensers in which the steam or vapour comes into direct contact with the cooling medium
- F28B3/04—Condensers in which the steam or vapour comes into direct contact with the cooling medium by injecting cooling liquid into the steam or vapour
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B9/00—Auxiliary systems, arrangements, or devices
- F28B9/04—Auxiliary systems, arrangements, or devices for feeding, collecting, and storing cooling water or other cooling liquid
- F28B9/06—Auxiliary systems, arrangements, or devices for feeding, collecting, and storing cooling water or other cooling liquid with provision for re-cooling the cooling water or other cooling liquid
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/10—Geothermal energy
Abstract
602725 Disclosed is a condenser for an axial flow exhaust type steam turbine and a geothermal power plant capable of ensuring nozzle pressure, reducing construction cost, and preventing water induction in the condenser for the axial flow exhaust type steam turbine. The condenser comprises a condenser unit which condenses steam exhausted from the steam turbine by directly contacting cooling water from a spray nozzle with the steam and a cooling tower which receives water condensed by the condenser unit, cools the condensed water with air-cooling to generate the cooling water, and accumulates the cooling water. A water circulating pipe which supplies water condensed by the condenser unit to the cooling tower and a water return circulating pipe which supplies the cooling water received and accumulated by the cooling tower to the condenser unit. A pump is connected to the water return circulating pipe performs so that the required pressure of the spray nozzle is equal to a value which is obtained by subtracting a static head difference between the upper most height for installing a spray nozzle of the condenser unit and a water surface level of the cooling tower from the pressure difference between the surface pressure in the cooling tower and the inner pressure of the condenser unit. A valve is connected to, and is capable of shutting-off the water return circulating pipe. nser unit which condenses steam exhausted from the steam turbine by directly contacting cooling water from a spray nozzle with the steam and a cooling tower which receives water condensed by the condenser unit, cools the condensed water with air-cooling to generate the cooling water, and accumulates the cooling water. A water circulating pipe which supplies water condensed by the condenser unit to the cooling tower and a water return circulating pipe which supplies the cooling water received and accumulated by the cooling tower to the condenser unit. A pump is connected to the water return circulating pipe performs so that the required pressure of the spray nozzle is equal to a value which is obtained by subtracting a static head difference between the upper most height for installing a spray nozzle of the condenser unit and a water surface level of the cooling tower from the pressure difference between the surface pressure in the cooling tower and the inner pressure of the condenser unit. A valve is connected to, and is capable of shutting-off the water return circulating pipe.
Description
PATENTS FORM NO. 5 Our ref: CHW 234518NZPR
NEW ZEALAND
S ACT 1953
COMPLETE SPECIFICATION
Condenser for axial flow exhaust type steam e and geothermal power plant having
the same
We, Kabushiki Kaisha Toshiba, a Japanese company of 1-1, Shibaura 1-Chome,
Minato-ku, Tokyo, Japan hereby declare the invention, for which we pray that a patent may be
granted to us and the method by which it is to be performed, to be particularly described in and
by the following statement:
(followed by page 1a)
CONDENSER FOR AXIAL FLOW EXHAUST TYPE STEAM TURBINE
AND GEOTHERMAL POWER PLANT HAVING THE SAME
CROSS NCE TO RELATED APPLICATION
This application is based upon and claims benefit of
priority from the se Patent Application No. 2011-219956,
filed on r 4, 2011, the entire contents of which are
incorporated herein by reference.
BACKGROUND OF THE INVENTION
FIELD OF THE INVENTION
The present ion relates to a condenser for an axial
flow exhaust type steam turbine used in a rmal power plant
or the like and a geothermal power plant having such a condenser.
RELATED ART
In a geothermal power plant, there is provided a condenser
which collects condensate by cooling and condensing exhaust after
a steam turbine is rotated by utilizing natural steam generated by
geothermal heat. A direct-contact type in which cooling water is
directly ted to exhaust from the steam turbine is included in
the condenser. Further, the -contact type condenser unit has
a tray type and a spray type in which cooling water is contacted to
exhaust by being directly sprayed by a spray.
The spray nozzle type includes a plurality of s installed
at appropriate positions in the condenser unit to splay circulating
water with the spray nozzles in the condenser unit.
Each nozzle is required to ensure pressure necessary for the
splaying. The pressure must be ensured even for a nozzle
3O installed at the uppermost part.
Here, requiring pressure of a nozzle is indicated as following
sion (1).
Nozzle requiring pressure II pressure difference (surface
pressure in a cooling tower (atmospheric pressure) — inner
pressure of a condenser unit (being lower than atmospheric
(followed by page 2)
difference (uppermost height for installing a spray nozzle of the
condenser unit — a water surface level of the cooling tower) (1)
As described above, it is necessary for the installation height
of the condenser unk and the cooHng tower to confider the
re dfiference beUNeen the Stuface pressure in the cooHng
tower and the inner pressure of the condenser unit, the pressure
loss at piping and a control valve, and the static head difference
between the spray nozzle height and the water surface level of the
cooHngtowen
In expression (1), the pressure difference between the inner
pressure of the surface re in the cooling tower and the inner
pressure ofthe condenser unn and the pressureloss atthe pufing
and the l valve are determined by system designing. There
arises a necessity to lower an installation position of the spray
nozzle to ensure the nozzle requiring pressure in consideration of
the static head difference between the uppermost height for
installing the spray nozzle of the condenser unit and the water
surface level of the cooling tower. As a result, there has been a
m that construction cost is sed owing to deepened
excavation for the condenser unit.
Further, a conventional geothermal power plant mainly
adopts a downward exhaust type to perform exhausting downward
from a steam turbine. Therefore, it is not required to take
measures to prevent a phenomenon that cooling water inflows from
a water return circulating pipe to the steam turbine, that is, water
induction. r, with the rd exhaust type, it is
required to m excavation for a condenser unit to a position
being lower than the steam turbine, so that construction cost is
increased.
Recenfly,to fintherlessen pressurelosslTonia finahstage
blade outlet of a steam turbine to a condenser unit for reducing
construction cost, an axial flow exhaust type to directly introduce
exhaust from a rear side of the final-stage blade of the steam
turbhweis beconfing popLHarforthe seriJnkinstaHed atthe
same level as the steam turbine which is an axial flow exhaust
type.
In a case of adopting such an axial flow exhaust type, it is
required to take measures for a level of water accumulated in the
condenser unit, that is, a hot well level, to prevent occurrence of
turbine water ion due to cooling water inflowing to the
condenser unit until a control valve installed at a water return
circulating pipe is fully closed when a water circulating pump is
ntly stopped.
Specifically, the hot well level of the condenser unit must be
set in consideration of an increasing level due to a cooling water
inflow amount to the condenser unit from a lowermost vane level of
the stage blade of the steam turbine.
Here, a higher water level of the cooling tower causes larger
static head difference t the hot well level of the ser
unit, resulting in increase of the cooling water amount inflowing to
the condenser unit during the time until the l valve is fully
closed. In accordance with the above, necessary height for storing
cooling water is increased, so that the hot well level is required to
be lowered. Accordingly, there has been a problem that
construction cost is increased due to deepened excavation for the
condenser unit.
Japanese Patent Application Laid-Open No. 2001-193417
described below ses a —contact type condenser for a
conventional axial flow exhaust type steam turbine. The
condenser prevents inflow of cooling water from a cooling tower to
a condenser unit at the time of water circulating pump stopping
and prevents water ion by forming a rising portion at a water
return circulating pipe and connecting a siphon breaker having a
branched pipe and a valve to the ty of a peek of the rising
portion.
SUMMARY OF THE INVENTION
However, the technology disclosed in Japanese Patent
Application Laid-Open No. 2001-193417 which prevents water
induction in a direct-contact type condenser for an axial flow
exhaust type steam turbine cannot solve the problem of
construction cost increase due to deepened excavation for a
condenser unit to ensure nozzle requiring pressure. Alternatively
it is an object to at least provide the public with a useful choice.
To address any one of the above issues, the present
invention provides a condenser for an axial flow exhaust type
steam turbine and a geothermal power plant capable of ensuring
nozzle requiring pressure, reducing construction cost, and r,
preventing water induction in the condenser for the axial flow
exhaust type steam turbine.
According to one aspect of the present ion, there is
provided a condenser for an axial flow exhaust type steam e
comprising:
a condenser unit which condenses steam exhausted from
the steam turbine by ly contacting cooling water from a spray
nozzle with the steam;
a cooling tower which receives water condensed by the
condenser unit, cools the condensed water with air-cooling to
generate the cooling water, and accumulates the cooling water;
a water circulating pipe which supplies water condensed by
the condenser unit to the cooling tower;
a water return circulating pipe which supplies the cooling
water received and accumulated by the g tower to the
condenser unit; and
wherein a pump is connected to the water return circulating
pipe.
According to r aspect of the invention, there is
provided a geothermal power plant comprising:
the condenser for an axial flow exhaust type steam turbine
according to any one of claims 1 to 6;
the steam e which receives steam and which exhausts
work-performed steam to the condenser; and
a generator which generates power as receiving rotational
energy from the steam turbine.
Unless the context clearly requires ise, throughout
the description and claims the terms “comprise”,
“comprising” and the like are to be construed in an inclusive
sense, as opposed to an exclusive or exhaustive sense. That is,
in the sense of “including, but not limited to”.
BRIEF DESCRIPTION OF THE DRAWINGS
is a layout diagram illustrating a structure of a
ser for an axial flow exhaust type steam turbine and a
geothermal power plant according to a first embodiment of the
present ion;
is an explanatory view illustrating relation between
hoisting height of a water ating pump and height of a turbine
building for the condenser for an axial flow exhaust type steam
turbine and the geothermal power plant according to the first
embodiment of the present invention;
is a layout m illustrating a structure of a
condenser for an axial flow exhaust type steam turbine and a
geothermal power plant according to a second embodiment of the
50243PSCH
present invention; and
is a layout diagram illustrating a ure of a
condenser for an axial flow exhaust type steam turbine and a
geothermal power plant according to a third embodiment of the
present invention.
ED DESCRIPTION OF THE EMBODIMENTS
Hereafter, a condenser for an axial flow exhaust type steam
e and a geothermal power plant according to ments of
the present invention will be described with reference to the
drawings.
(First Embodiment)
A condenser for an axial flow exhaust type steam turbine
and a geothermal power plant having the same according to a first
embodiment of the present invention will be described by using illustrating a structure thereof.
Steam inflows to a steam turbine 1 from steam piping (not
illustrated), and then, inflows to a condenser unit 2 being a splay
direct-contact type as being exhausted after ming work at
the steam turbine 1.
A spray nozzle 3 is arranged at the inside of the condenser
unit 2 and cooling water supplied from a cooling tower 4 via a
water return circulating pipe 5 is splayed and is directly ted
to steam. Accordingly, steam exhausted from the steam turbine 1
is condensed to be condensate and is accumulated at a lower part
of the condenser unit 2 along with the cooling water.
The accumulated water is pressurized by a water circulating
pump 6 and is fed to a cooling tower sprinkling pipe 7 which is
installed to an upper part of the cooling tower 4 while a flow
amount thereof is adjusted by a control valve 9. Then, the water
is sprinkled and cooled with air-cooling and is accumulated at a
lower part of the cooling tower 4.
The water accumulated at the g tower 4 is returned to
the spray direct-contact type condenser unit 2 as cooling water via
a pump 8 at the water return circulating pipe 5 as described later.
Here, as illustrated in levels of the respective
elements are indicated as s.
L1: Water surface level of the cooling tower 4
L2: Uppermost height for installing the spray nozzle 3 at the
inside of the condenser unit 2
L3: Installation level (excavation level) of the condenser unit
L4: Installation level of the cooling tower 4
L5: Maximum height of the cooling tower 4
L6: Hot well level of the condenser unit 2
L7: Final-stage blade vane level of the steam turbine 1
L8: lation level (height of a rotary shaft) of the steam
turbine 1
L9: Sprinkling pipe installation level of the cooling tower 4
Requiring re APl of the spray nozzle 3 is indicated as
ing sion (2) based on abovementioned expression (1).
APl = pressure difference (surface pressure in the cooling
tower (atmospheric pressure) — inner pressure of the condenser
unit (being lower than atmospheric pressure)) — re loss (at
valves and ) — static head difference AP2 (L2 (uppermost
height for installing the spray nozzle of the condenser unit) — L1
(water surface level of the cooling tower)) (2)
The first embodiment is characteristic in installing the pump
8 to the water return circulating pipe 5 for assisting to ensure the
requiring pressure APl of the spray nozzle 3 in expression (2).
With the above, since the requiring pressure API is not necessarily
ied by the static head difference AP2, following effects can be
obtained.
i) Owing to exclusion of necessity to lower the installation
height L2 of the spray nozzle of the condenser unit 2 and to lower
the installation level (excavation level) L3 of the condenser unit 2
accordingly in consideration of the static head difference AP2,
construction cost can be reduced.
atively, owing to exclusion of necessity to heighten the
installation level L4 of the cooling tower 4 or the height L5 of the
cooling tower 4 for heightening the water surface level L1 of the
cooling tower 4 in consideration of the static head difference AP2,
tion due to the static head difference APZ is excluded and
construction cost can be reduced.
ii) It becomes possible to lessen the static head ence
APZ. Accordingly, a flow amount of cooling water inflowing from
the cooling tower 4 to the condenser unit 2 until the control valve 9
is fully-closed is decreased. As a result, water induction can be
prevented even when level difference (L7—L6) between the
final—stage blade vane level L7 of the steam turbine 1 and the hot
well level L6 of the condenser unit 2 is set small.
With the above, it becomes le to heighten the
installation level (excavation level) L3 of the condenser unit 2, that
is, to lessen an excavation amount or to lower the installation level
L8 of the steam turbine 1. Accordingly, following effects can be
obtained.
a) Since the excavation level L3 of the condenser unit 2 can
be heightened by heightening the hot well level L6 of the
condenser unit 2, an effect to reduce construction cost can be
obtained.
b) rates a state that the steam turbine 1, the
condenser unit 2, and the water ating pump 6 are installed in
a turbine building 20. In a case of a failure, it is necessary to hoist
and convey the water circulating pump 6 in the e building 20
with a crane or the like. In a case that the water circulating pump
6 is installed indoors along with the steam turbine 1 as described
above, it is required to ine height of the turbine building 20
in consideration of hoisting height when the water circulating pump
6 fails and allowable height H of a conveyance route to pass above
ent existing with the maximum height in the turbine
building 20.
3O As illustrated in in a case that the equipment with
the maximum height in the turbine building 20 is auxiliary to the
steam turbine 1, for example, as being a turbine casing which
covers the steam turbine 1 and the condenser unit 2 in an
integrated manner, a phase separation generating line between a
generator (not rated) and the steam turbine 1, or the like, an
effect to reduce construction cost can be obtained as lowering the
height of the entire building by lowering the installation level L8 of
the steam turbine 1.
As described in above a), owing to ling the pump 8 to
the water return circulating pipe 5, the hot well level L6 of the
condenser unit 2 can be heightened.
Accordingly, the static head difference t the cooling
tower sprinkling pipe 7 which is installed to the upper part of the
cooling tower 4 becomes small and pump head of the water
circulating pump 6 can be lessened. Further, as bed in
above i), since the height L5 of the cooling tower 4 is not required
to be heightened, the installation level L9 of the cooling tower
sprinkling pipe 7 is not heightened accordingly and pump head of
the water circulating pump 6 can be lessened. Therefore,
construction cost can be reduced.
(Second Embodiment)
A condenser for an axial flow exhaust type steam turbine
and a rmal power plant having the same according to a
second embodiment of the present invention will be described by
using illustrating a structure thereof. Here, the same
numeral is given to the same structural element as in the first
embodiment illustrated in and redundant ption will not
be repeated.
In addition to the structure of the first embodiment, the
second embodiment has difference therefrom in further including a
hydraulic or tic shut-off valve 10 as well as the pump 8 at
the water return circulating pipe 5. Being related to the shut—off
valve 10, a failure detecting device 31 and a control device 32 are
The failure detecting device 31 detects a failure in a case
3O that either or both of the water ating pump 6 and the control
valve 9 fail. When the failure detecting device 31 detects the
failure, the control device 32 controls the shut-off valve 10 to be
closed.
With the above, in a case that the water circulating pump 6
fails, that the control valve 9 s incapable of adjusting a flow
amount, or that the hot well level L6 is raised with failures of the
water circulating pump 6 and the control valve 9, inflow of
circulating water from the cooling tower 4 to the condenser unit 2
can be immediately shut—off by g the shut-off valve 10
led at the water return circulating pipe 5. Accordingly, water
ion can be prevented even when ence between the
installation level L8 of the turbine 1 and the hot well level L6 which
is ted by the inflow amount of circulating water to the
condenser unit 2 is set small. Thus, as described in the first
embodiment, construction cost can be reduced by heightening the
excavation level L3 of the condenser unit 2 as heightening the hot
well level L6.
(Third Embodiment)
A condenser for an axial flow exhaust type steam turbine
and a geothermal power plant having the same according to a third
embodiment of the present invention will be described by using illustrating a structure thereof. Here, the same numeral is given
to the same structural element as in the first embodiment
illustrated in and redundant description will not be repeated.
The third embodiment differs from the second embodiment
2 in that a control valve 11 is arranged at the water return
circulating pipe 5 d of the shut-off valve 10. Being related to
the control valve 11, a failure detecting device 31 and a control
device 32 are ed.
The failure detecting device 31 detects a failure in a case
that either or both of the water circulating pump 6 and the control
valve 9 fail. When the failure detecting device 31 s the
failure, the control device 32 controls adjustment of a flow amount
at the control valve 11.
In a case that the water circulating pump 6 fails or that the
hot well level L6 is raised with incapability of flow amount adjusting
by the control valve 9, an inflow amount of circulating water to the
condenser unit 2 can be regulated by controlling adjustment of the
flow amount at the control valve 11 installed at the water return
circulating pipe 5 instead of the shut-off valve 10. The above
reduces difference between the installation level L8 of the steam
turbine 1 and the hot well level L6 which is regulated by the inflow
amount of circulating water to the condenser unit 2, that is,
required height for storage of cooling water. Accordingly, water
induction can be prevented even when the difference between the
levels L6 and L8 is set small.
Thus, since the excavation level L3 of the condenser unit 2
is not required to be lowered owing to needlessness of lowering the
hot well level L6, construction cost can be reduced.
While certain embodiments have been described, these
embodiments have been ted by way of example only, and
are not intended to limit the scope of the t invention.
Indeed, the novel systems described herein may be embodied in a
variety of other forms; furthermore, various omissions,
tutions and changes in the form of the systems bed
herein may be made without departing from the spirit of the
inventions. The accompanying claims and their equivalents are
intended to cover such forms or modifications as would within the
scope and the spirit of the present inventions.
Claims (9)
1. A ser for an axial flow exhaust type steam turbine comprising: a condenser unit which condenses steam exhausted from the steam e by directly contacting cooling water from a spray nozzle with the steam; a cooling tower which es water condensed by the ser unit, cools the condensed water with air-cooling to generate the cooling water, and accumulates the cooling water; a water circulating pipe which supplies water condensed by the condenser unit to the cooling tower; a water return circulating pipe which supplies the cooling water received and accumulated by the cooling tower to the condenser unit; and wherein a pump is connected to the water return circulating pipe.
2. The condenser for an axial flow exhaust type steam turbine according to claim 1, wherein the pump performs so that the required pressure of the spray nozzle is equal to a value which is obtained by subtracting a static head difference between the upper most height for installing a spray nozzle of the condenser unit and a water surface level of the cooling tower from the re difference between the surface pressure in the cooling tower and the inner pressure of the condenser unit.
3. The condenser for an axial flow t type steam turbine according to claim 1 or claim 2, further comprising a valve connected to, and e of shutting-off the water return circulating pipe.
4. The condenser for an axial flow exhaust type steam turbine according to claim 1 or claim 2, wherein a first control valve to adjust a flow amount is connected to the water return circulating pipe.
5. The condenser for an axial flow exhaust type steam turbine according to claim 3, further comprising: a water ating pump which supplies water condensed by the ser unit to the cooling tower connected to the water circulating pipe; a second control valve which adjusts a flow amount of water condensed by the condenser unit; a failure detecting device which detects a failure of each of the water circulating pump and the second control valve; and a control device which closes the valve capable of shutting-off when a failure of either or both of the water circulating pump and the second control valve is detected by the e detecting device.
6. The condenser for an axial flow t type steam turbine ing to claim 4, further comprising: a water circulating pump which supplies water condensed by the condenser unit to the cooling tower connected to the water circulating pipe; a second l valve which adjusts a flow amount of water condensed by the condenser unit; a failure detecting device which detects a failure of each of the water circulating pump and the second control valve; and a control device which adjusts a flow amount through the water return circulating pipe with the first control valve when a failure of either or both of the water circulating pump and the second control valve is ed by the failure detecting device.
7. A geothermal power plant, sing: the condenser for an axial flow exhaust type steam turbine according to any one of claims 1 to 6; the steam turbine which receives steam and which exhausts work-performed steam to the condenser; and a tor which generates power as receiving rotational energy from the steam turbine.
8. A condenser substantially as described herein with reference to the accompanying drawings. 5
9. A geothermal power plant comprising a condenser substantially as described herein with reference to the accompanying drawings. HIGEI 47 < 04 > mm;>0._. IE>mI_ mmk<>> z main. amt/>8. 023000 OZZXZEQm ZOE.<:3<._.mZ_ awe/0H Jm>mj 023000 kill; 2072:7215; .3 m 023000 d5: HIOEI N4 FmOEmmEnB OZ_1.:_<._.mZ_ ijNOZ mom ><mam 3.: 4m>mj m4 ZO_H<44<FmZ
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011-219956 | 2011-10-04 | ||
| JP2011219956A JP2013079603A (en) | 2011-10-04 | 2011-10-04 | Condensing equipment for axial flow exhaust type steam turbine and geothermal power plant |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| NZ602725A NZ602725A (en) | 2013-08-30 |
| NZ602725B true NZ602725B (en) | 2013-12-03 |
Family
ID=
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US20130081393A1 (en) | Condenser for axial flow exhaust type steam turbine and geothermal power plant having the same | |
| CN1847626A (en) | Variable pressure-controlled cooling scheme and thrust control arrangements for a steam turbine | |
| JP5230683B2 (en) | High temperature drain recovery system | |
| US20080022699A1 (en) | Air-conditioning system and method of installing energy recovery apparatus | |
| CN104153830B (en) | The control method and control system of a kind of feed pump turbine | |
| CN107342587A (en) | A kind of dc power in real time can hoisting power computational methods | |
| JP2012184735A (en) | Composite cycle plant | |
| JP4937822B2 (en) | Condenser vacuum degree control system and power plant including the system | |
| NZ602725B (en) | Condenser for axial flow exhaust type steam turbine and geothermal power plant having the same | |
| CN107419789A (en) | The drainage system and water discharge method of the turbine-generator units in the higher river of tailwater level | |
| JP5783458B2 (en) | Increased output operation method in steam power plant | |
| KR101160772B1 (en) | Backflow prevent of advanced passive auxiliary feed-water system for pressurized water reactor | |
| JP2011153799A (en) | Once-through exhaust heat recovery boiler | |
| JP2016035254A (en) | Decompression energy recovery device in gas pipeline | |
| JPS63117107A (en) | Auxiliary steam device | |
| KR101544446B1 (en) | The degree of a vacuum control apparatus of condenser | |
| JP2013144967A (en) | Gland steam seal device of steam turbine | |
| US10533460B2 (en) | Multi stage steam turbine for power generation | |
| JPH0842803A (en) | Water feeding device for double pressure type exhaust heat recovery boiler | |
| JP7287367B2 (en) | Binary geothermal power generation system | |
| JP2006312882A (en) | Steam turbine power generation plant and its operation method | |
| KR101217835B1 (en) | Boiler safety apparatus of steam power plant | |
| JP4848386B2 (en) | Power plant condensate system | |
| JP6013054B2 (en) | Condensation system damage prevention device and damage prevention method | |
| KR20240103155A (en) | Differential pressure type water level measuring appartus for preventing water draining from the condensate port |