NZ622394B2 - Binary power generation system - Google Patents
Binary power generation system Download PDFInfo
- Publication number
- NZ622394B2 NZ622394B2 NZ622394A NZ62239412A NZ622394B2 NZ 622394 B2 NZ622394 B2 NZ 622394B2 NZ 622394 A NZ622394 A NZ 622394A NZ 62239412 A NZ62239412 A NZ 62239412A NZ 622394 B2 NZ622394 B2 NZ 622394B2
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- NZ
- New Zealand
- Prior art keywords
- medium
- steam
- water
- liquid
- turbine
- Prior art date
Links
- 238000010248 power generation Methods 0.000 title claims abstract description 36
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 150
- 239000007788 liquid Substances 0.000 claims abstract description 139
- 238000007599 discharging Methods 0.000 claims description 2
- 238000001816 cooling Methods 0.000 claims 1
- 239000007789 gas Substances 0.000 description 43
- 238000010586 diagram Methods 0.000 description 6
- 241000196324 Embryophyta Species 0.000 description 5
- 125000002842 L-seryl group Chemical group O=C([*])[C@](N([H])[H])([H])C([H])([H])O[H] 0.000 description 5
- 238000009835 boiling Methods 0.000 description 5
- 238000004891 communication Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 5
- 238000000034 method Methods 0.000 description 5
- 239000002803 fossil fuel Substances 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000006011 modification reaction Methods 0.000 description 3
- 238000009833 condensation Methods 0.000 description 2
- 230000005494 condensation Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 230000008929 regeneration Effects 0.000 description 2
- 238000011069 regeneration method Methods 0.000 description 2
- 238000010792 warming Methods 0.000 description 2
- 241000229754 Iva xanthiifolia Species 0.000 description 1
- 229940035295 Ting Drugs 0.000 description 1
- IJDNQMDRQITEOD-UHFFFAOYSA-N butane Chemical compound CCCC IJDNQMDRQITEOD-UHFFFAOYSA-N 0.000 description 1
- 239000001273 butane Substances 0.000 description 1
- 230000001808 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000003247 decreasing Effects 0.000 description 1
- 238000001704 evaporation Methods 0.000 description 1
- CBENFWSGALASAD-UHFFFAOYSA-N ozone Chemical compound [O-][O+]=O CBENFWSGALASAD-UHFFFAOYSA-N 0.000 description 1
- OFBQJSOFQDEBGM-UHFFFAOYSA-N pentane Chemical compound CCCCC OFBQJSOFQDEBGM-UHFFFAOYSA-N 0.000 description 1
- 230000000630 rising Effects 0.000 description 1
- 239000011555 saturated liquid Substances 0.000 description 1
- 238000010025 steaming Methods 0.000 description 1
- 230000005514 two-phase flow Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
- 230000003313 weakening Effects 0.000 description 1
Classifications
-
- 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
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
- F01K23/04—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled condensation heat from one cycle heating the fluid in another cycle
-
- 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
- F01K5/00—Plants characterised by use of means for storing steam in an alkali to increase steam pressure, e.g. of Honigmann or Koenemann type
- F01K5/02—Plants characterised by use of means for storing steam in an alkali to increase steam pressure, e.g. of Honigmann or Koenemann type used in regenerative installation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
- F03G7/00—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for
- F03G7/04—Mechanical-power-producing mechanisms, not otherwise provided for or using energy sources not otherwise provided for using pressure differences or thermal differences occurring in nature
-
- 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
- F24—HEATING; RANGES; VENTILATING
- F24T—GEOTHERMAL COLLECTORS; GEOTHERMAL SYSTEMS
- F24T10/00—Geothermal collectors
- F24T10/20—Geothermal collectors using underground water as working fluid; using working fluid injected directly into the ground, e.g. using injection wells and recovery wells
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
-
- 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
Disclosed is a binary power generation system. The binary power generation system comprises: a first pressure reducing steam-liquid separator (12) which reduces the pressure of geothermal heat source water to separate the geothermal heat source water into water steam and liquid hot water; a steam turbine (14) driven by the water steam; a condenser/evaporator (20) configured to transfer heat of the water steam discharged from the steam turbine (14) to the liquid medium so that the water steam is condensed and the liquid medium is evaporated; a medium superheater (16) that transfers heat from the hot liquid water to the evaporated liquid medium to generate a superheated vapor medium; a medium turbine (31) driven by the superheated vapour medium; a second pressure reducing steam-liquid separator (17) that reduces pressure of the hot liquid water from the medium superheater (16) to separate the hot liquid water into water steam and hot liquid water, where the water steam separated by the second pressure reducing steam-liquid separator is led into the condenser/evaporator (20) along with the water steam discharged from the steam turbine (14); a gas cooler (22) that further cools gas remaining in the condenser/evaporator (20) by using the superheated vapor medium discharged from the medium turbine (31) as a cold source to separate and discharge noncondensable gas contained in the gas; and at least one generator (37) driven by the steam turbine (14) and the medium turbine (31). rbine (14) driven by the water steam; a condenser/evaporator (20) configured to transfer heat of the water steam discharged from the steam turbine (14) to the liquid medium so that the water steam is condensed and the liquid medium is evaporated; a medium superheater (16) that transfers heat from the hot liquid water to the evaporated liquid medium to generate a superheated vapor medium; a medium turbine (31) driven by the superheated vapour medium; a second pressure reducing steam-liquid separator (17) that reduces pressure of the hot liquid water from the medium superheater (16) to separate the hot liquid water into water steam and hot liquid water, where the water steam separated by the second pressure reducing steam-liquid separator is led into the condenser/evaporator (20) along with the water steam discharged from the steam turbine (14); a gas cooler (22) that further cools gas remaining in the condenser/evaporator (20) by using the superheated vapor medium discharged from the medium turbine (31) as a cold source to separate and discharge noncondensable gas contained in the gas; and at least one generator (37) driven by the steam turbine (14) and the medium turbine (31).
Description
DESCRIPTION
BINARY'POWER GENERATION SYSTEM
TECHNICAL FIELD
Embodiments of this invention relate to a binary power generation
system using geothermal heat.
BACKGROUND ART
The greenhouse effect from 002 has ly been pointed out as
one of the causes of the global warming phenomenon. Immediate actions
are needed to protect the earth's environment. C02 sources include human
activities of burning fossil fuels, and there is an increasing demand for
emission control. As a result, new construction of thermal power plants and
the like using large amounts of fossil fuels has been ting because of
high 002 emissions.
Demand is increasing for power generation s using
renewable energies that produce no 002, such as solar light, solar heat, wind
power, geothermal heat, and tidal power. Of these, power generation
systems using geothermal steam and geothermal water have been
commercialized since the 1950s. With high construction costs, geothermal
power plants used to decline in the age of decreasing foSsil fuel costs,
s the demand has been increasing again in recent years. Some of
existing geothermal power plants are shifting from a flash geothermal power
generation system in which a steam turbine is driven by geothermal steam
to a binary geothermal power generatiOn system in which hot water is used
as a heat source to evaporate an organic working medium for generation
because the thermal energy of the rmal steam decreases gradually.
Such a binary geothermal power generation System uses a medium
having a boiling point lower than that of water as the working medium.
Examples of the low-boiling medium include chlorofluorocarbons which were
used as the working medium of refrigerators until 1990. Since existing
chlorofluorocarbons harm the ozone layer and there has been found no
low-boiling medium to be a workable alternative, the binary rmal
power generation system has not been actively put to cal use in Japan.
Under the circumstances, binary power generation systems using
flammable but produced-in' volume butane (C4H10) 0r pentane (CsHlZ) as the
working medium have been commercialized.
In a que disclosed in Patent Document 1, a pressure reducing '
steam-liquid separator flashes and tes geothermal water into steam
and hot liquid water. The hot water having lower enthalpy preheats the
working medium, and the flashed steam evaporates the working medium.
Such a system is ive if the proportion of the flashed steam is small.
When c g vapor medium is expanded in a turbine, the
degree Lof superheat increases and gas (vapor) having a temperature higher
than a condensation temperature in a condenser is condensed. In a
technique disclosed in Patent Document 2, preheater outlet liquid medium is
injected into an intermediate stage of a Working medium turbine so that the
gas having a high degree of superheat is mixed with the saturated liquid.
As a , the energy of the degree of superheat can be used to increase the
driving flow rate of the turbine and improve the cycle efficiency.
In a technique sed in Patent Document3, a steam turbine is
driven by flashed steam from a geothermal water pressure reducing
steam-liquid separator. The exhausted steam evaporates a medium, and
hot water separated from the pressure reducing steam-liquid separator
superheats the medium. Proposed modifications e the following:
(1) Install a rator at the outlet of the medium turbine.
(2) Provide a age medium turbine, and reheat the vapor
medium by the hot water from the outlet of a superheater.
”In a technique disclosed in Patent Document 4 and a technique
sed in Patent Document 5, a steam turbine is driven by part of flashed
steam from a geothermal water pressure reducing steam-liquid separator.
The rest of the flashed steam evaporates a medium. The exhausted steam
from the steam turbine and hot water from the pressure reducing
steam-liquid separator preheat the medium. A regenerator'is arranged at
the outlet of a medium turbine. A modified embodiment is disclosed in
which a two-stage medium turbine is provided and the vapor medium is
reheated by hot water from the outlet of a superheater.
A technique disclosed in Patent Document 6 deals with a system
that is not limited to geothermal power generation but also takes into
account solar heat and the exhaust heat of thermal power tion etc.
Two types of media, one for high temperature and the other for low
temperature, are used to constitute a cascaded Rankine cycle, which is a
basic form of cascade type.
' Patent nt 7 discloses one including a plurality of
evaporators with different pressures.
[DOCUMENTS OF PRIORART]
[PATENT DOCUMENT]
Patent nt 13 U.S. Patent No. 598
Patent Document 21 U.S. Patent No. 5,531,073
Patent Document 31 U.S. Patent No. 6,009,711
Patent Document 43 U.S. Patent No. 7,775,045
Patent Document 53 U.S. Patent No. 7,797,940
Patent Document 63 U.S. Patent No. 7,823,386
Patent Document 71 Japanese Patent Application Laid-Open
Publication No; 2009-221961
SUMMERY OF THE INVENTION
PROBLEMS TO BE SOLVED BY THE INVENTION
As bed above, demand for geothermal power tion has
been increasing from the Viewpoint of global warming. Power plants have
already been constructed in locations where high quality geothermal s
are and in locations Where geothermal sources have high enthalpy and
provide a highproportion of flashed steam when reduced in pressure. On
existing geothermal power plants, it is reported that the heat sources in the
entire ons are weakening, and the proportion of steam is on the
decrease and the proportion of hot water on the increase. Under the
circumstances, a binary geothermal power generation system using not a
steam e but a low-boiling working medium such as an organic medium
is advantageous. Since geothermal s are seldom fully depleted of
steam to produce. only hot water, a power generation system combining a
flash type and a binary type is the most ageous.
Among the foregoing systems combining a flash geothermal power
generation system and a binary geothermal power generation system are
ones that reduce the pressure of (flash) the geothermal source before using
only the hot water for binary power generation, and ones that use both the
exhaust of the turbine driven by the flashed steam and the hot water for
binary power generation. The binary power generation systems that
perform binary power generation by using only the hot water as a heat
source have a small capacity, a low output rate, and a high unit cost of binary
power generation.
Assume a system in which a turbine driven by flashed steam has a
back pressure higher than or equal to atmospheric pressure. The latent
heat of the steam of 100 s centigrade or above ates a working
medium such as an organic . The vapor medium is superheated by
hot water from the outlet of a pressure reducing steam-liquid separator,
having a temperature higher than that of the exhausted e steam, and
drives a medium turbine. The system includes a ratOr that performs
heat exchange n the superheated vapor from the outlet of the medium
turbine and liquid medium from a condenser. In such a , the heat
exchange is performed between the vapor medium from the turbine outlet,
which originally has a high degree of superheat, and the liquid medium.
This increases pressure loss on the vapor medium side of the regenerator
and increases the outlet pressure of the medium turbine, failing to provide a
high effect. ln addition, the exhaust gas of the steam turbine ally
contains noncondensable gas, which needs to be extracted and collected.
Embodiments of the present invention have been achieved in View
of the foregoing circumstances, and it is an object thereof to se the
efficiency of a binary power generation system that combines a geothermal
flash vapor cycle and a non-water working medium cycle.
MEANS FOR SOLVING THE PROBLEMS
. In order to solve the problems, according to an aspect of the present
invention, there is provided a binary power generation system comprising: a
first pressure reducing steam-liquid separator that reduces pressure of
geothermal heat source water to separate geothermal heat source water into
water steam and hot liquid water; a steam turbine that is driven by the
water steam; a medium turbine that is driven by vapor medium obtained by
evaporating liquid medium by using the geothermal heat source water as a
heat source; a condenser/evaporator that is configured to transfer heat of the
water steam discharged from the steam turbine to the liquid medium so that
the water steam is condensed and the liquid medium is evaporated; a gas
cooler that further cools gas ing in the condenser/evaporator by using
a medium discharged from the medium turbine as a cold source, thereby
' separating and discharging noncondensable
gas contained in the gas; and at
least one generator to be driven by the steam turbine and the medium
turbine.
According to another aspect of the present invention, there is
provided a binary power generation system comprising; a first pressure
reducing steam-liquid tor that reduces pressure of geothermal heat
source water to separate geothermal heat source water into water steam and
hot liquid water; a steam turbine that is driven by the water steam; a high
pressure evaporator that evaporates a g medium to generate high
pressure vapor medium by using the geothermal heat source water as a heat
source; a high pressure medium turbine that is driven by the high re
vapor medium; a condenser/evaporator that is configured to mix vapor
medium. discharged from the high pressure medium turbine with liquid
medium supplied separately from the vapor medium, and transfer heat of
the water steam discharged from the steam e to the working medium
so that the water steam is condensed and low pressure vapor medium having
a re lower than that of the high pressure vapor medium is generated;
> a low re medium turbine that is driven by the low pressure vapor
medium; a ser that condenses vapor medium discharged from the low
pressure medium turbine to generate the liquid medium; and at least one
generator to be driven by the steam turbine, the high pressure medium
turbine, and the low pressure medium turbine.
BRIEF DESCRIPTION OF THE DRAWINGS
is a system diagram g a configuration of a first
embodiment of'the binary power generation system according to the present
invention.
is a system diagram showing a configuration of a second
embodiment of the binary power generation system according to the present
invention.
is a longitudinal sectional View showing a specific
configuration of a condenser/evaporator ing to the second embodiment.
is a system diagram showing a ration of a third
embodiment of the binary power generation system according to the present
invention.
EMBODIMENTS FOR CARRYING OUT THE INVENTION
, Embodiments of the present invention will be described below with
reference to the drawings. The same or similar parts will be designated by
common reference symbols. A redundant ption thereof will be
omitted.
The embodiments include a heat source water system along a flow
of supplied geothermal heat source water and a medium system which
operates by receiving heat from the heat source water system. An c
medium and the like having a boiling point lower than that of water at
heric pressure may be used as a working medium in the medium
system.
[FIRST EMBODIMENT]
is a system diagram showing a configuration of a first
embodiment of the binary power generation system according to the present
invention.
<Heat Source Water >
Initially, a configuration of a heat source water system will be
described along a flow of supplied geothermal heat source water.
Geothermal heat source water piping 11 is ted to a first
pressure ng steam-liquid separator (flasher) 12. Geothermal heat
source water supplied to the first pressure reducing steam-liquid separator
12 through the geothermal heat source water piping 11 is reduced in
pressure there, and separated into high pressure water steam and high
pressure hot water d water). The generated water steam. is sent to a
steam e 14 Via a water steam governing valve 13. Low pressure
steam having worked in the steam turbine 14 is discharged through steam
turbine return piping 15.
The high re hot water generated by the first pressure
reducing liquid tor 12 is sent to a medium superheater 16 and
further sent to a second pressure reducing steam-liquid separator 17. The
second pressure reducing steam-liquid separator 17 includes a pressure .
reducing valve 18 on the upstream side and a steam-liquid separator 19
connected downstream. The hot water sent to the second pressure reducing
steam-liquid separator 17 is separated here into low pressure water steam
and low pressure hot water (liquid water).
The low pressure water steam generated by the second pressure
reducing steam-liquid separator 17 joins the steam turbine return piping 15
and is sent to a condenser/evaporator 20. The low pressure water steam
- sent to the ser/evaporator 20 releases heat here, whereby 90 % or
more of the low pressure water steam is condensed into condensate (liquid
water). The condensate obtained by the condenser/evaporator 20 is sent to
a preheater 21 via condensate piping 50, and further releases heat here and
becomes water of lower temperature.
The low pressure water steam sent to the condenser/evaporator 20
contains a densable gas ent. The gas left u‘ncondensed in the
low pressure water steam sent to the condenser/evaporator 20 is sent to a
gas cooler 22 via gas cooler inlet piping 51. The gas is further cooled here,
and the remaining gas is emitted to the air as noncOndensable gas. The low
re hot‘water obtained by the second pressure reducing steam-liquid
separator 17 joins the condensate piping 50 and is sent to the ter 21.
<Medium System>
Next, a non-water medium system will be bed.
Vapor medium is supplied to the medium superheater 16. The
vapor medium receives heat from the high pressure hot water generated by
the first pressure reducing steam-liquid separator 12, whereby superheated
vapor medium is generated. The superheated vapor medium is supplied to
a medium turbine 31 via a vapor medium governing valve 30. Low pressure
vapor medium having worked in the medium turbine 31 is'cooled by a
regenerator 32, and further sent to a medium condenser 33, where the low
pressure vapor medium is cooled and condensed. The medium condenser 33
is cooled by a cold water system 85 including a cold water pump 34.
A medium pump 36 increases pressure of the liquid medium
condensed by the medium condenser 33. In the regenerator 32, the liquid,
medium increased in re by the medium pump 36 is heated by heat
exchange with the vapor medium that is sent from the medium turbine 31
. and yet to be condensed by the medium condenser 33. The heated liquid
medium is sent to the gas cooler 22. The gas cooler 22 transfers heat from
the noncondensable gas to the g medium. The liquid medium heated
by the gas cooler 22 is sent to the preheater 21. The preheater 21 transfers
heat from the hot water to the liquid medium to preheat the liquid medium.
The liquid medium preheated by the preheater 21 is sent to the
condenser/evaporator 20 via preheater liquid medium outlet piping 53. The
liquid medium is heated and evaporated here by latent heat occurring during
the condensation of the water steam, whereby vapor medium is generated.
The vapor medium is sent to the medium eater 16.
The steam turbine 14 and the medium turbine 31 are coaxially
coupled with a generator 37 and a generator 38, respectively.
_ According to the present embodiment, the noncondensable gas
component ned in the geothermal heat source water can be released to
the air from the gas cooler 22. As a result, the water condensed by the
condenser/evaporator 20 can be smoothly led to the preheater 21.
The low-temperature liquid medium coming out of the regenerator
32 is used as a cold source of the gas cooler 22. The cold heat enables
emission of highly-concentrated noncondensable gas. Theliquid medium
can also be heated for a regeneratiOn effect.
In such a manner, the ncy of the binary power generation
system combining a rmal flash steam cycle and a ter working
medium cycle can be increased.
. [SECOND EMBODIMENT]
is a system diagram showing a configuration of a second
embodiment of the binary power generation system according to the present
invention. is a longitudinal sectional View showing a specific
configuration of a condenser/evaporator ing to the second embodiment.
<Heat Source Water System>
Geothermal heat source water piping 11 is connected to a first
pressure reducing liquid separator 12. Geothermal heat source
water supplied to the first pressure reducing steam-liquid separator 12
through the rmal heat source water piping 11 is reduced in pressure
there and separated into high pressure water steam and high pressure hot :
water (liquid water). The water steam generated here is sent to a steam
turbine 14 via a water steam governing valve 13. Low pressure steam
having worked in the steam turbine 14 is rged through steam turbine
return piping 15.
The high pressure hot water (liquid water) generated by the first
pressure reducing steam-liquid separator 12 is sent to a high re
evaporator 41, where the high pressure hot water is cooled by heat exchange
with a g medium. The highvpressure hot water is then sent to a high
pressure preheater 42, where the high pressure hot water is further cooled
by heat exchange with liquid medium.
The low pressure water steam discharged from the steam turbine
14 through the steam turbine return pipe 15 is sent to a
condenser/evaporator 20. The low pressure water steam sent to the
ser/evaporator 20 releases heat here, whereby 90 % or more of the low
re water steam is condensed into condensate (liquid water). The
condensate ed by the condenser/evaporator 20 is sent to a preheater 21
Via condensate piping 50. The condensate further releases heat here and
becomes water of lower temperature.
The low pressure water steam sentto the condenser/evaporator 20
contains a noncondensable gas component. The gas left uncondensed in the
low pressure water steam sent to the condenser/evaporator 20 is sent to a
gas cooler 22 via gas cooler inlet piping 51. The gas is further cooled here,
and the remaining gas is emitted to the air as noncondensable gas.
m system>
Next, a non-water medium system will be described.
High temperature liquid medium, is supplied to the high pressure
evaporator 41. The high temperature liquid medium receives heat from the
high pressure hot water generated by the first pressure reducing
steam-liquid separator 12, whereby high pressure vapor medium is
generated. The high pressure vapor medium is sent to a high pressure
medium turbine 31a via a high re vapor medium governor value 30a.
Low pressure vapor medium having worked in the high pressure medium;
turbine 31a is sent to the condenser/evaporator 20 via high re medium
turbine return piping 52.
Liquid medium is supplied to the preheater 21, Where the liquid
medium receives heat from the condensate and is preheated. The liquid
medium preheated by the preheater 21 is sent to the condenser/evaporator
via preheater liquid medium outlet piping 53. In the
condenser/evaporator 20, the supplied liquid medium and the vapor medium
receive heat from the condensate to evaporate, y low pressure vapor
medium is generated. The low pressure vapor medium generated by the
ser/evaporator 20 is supplied to a low pressure medium turbine 31b
through low pressure vapor medium supply piping 54 and via a low pressure
vapor medium governing valve 30b. The low pressure vapor medium
supplied to the low pressure medium turbine 31b has a lower pressure than
the high pressure vapor medium supplied to the high pressure medium
turbine 31a.
The low pressure vapor medium having workedin the low pressure
medium e 31b is cooled by a regenerator 32. The ant is further
sent to a medium condenser 33 and further cooled to condense. The
medium condenser 33 is cooled by a cold water system 35 including a cold
water pump 34.
A medium pump 36 increases pressure of the medium condensed by
the medium condenser 33. In the regenerator 32, the liquid medium.
increased in pressure by the medium pump 36 is heated by heat exchange
with the vapor medium that is sent from the low pressure medium turbine
31b and yet to be condensed by the medium condenser 33. The heated
liquid medium is then sent to the preheater 21 through a branching point 43.
Part of the liquid medium passed through the branching point 43 is
not ed to the preheater 21 but pressurized by a medium pressurizing
pump 44 and sent to the gas cooler 22. The gas cooler 22 transfers heat
from the noncondensable gas to the liquid medium. The liquid medium'
heated by the gas cooler 22 is sent to the high re preheater 42. The
high pressure preheater 42 transfers heat from the hot water to the liquid
medium. The liquid medium is preheated and sent to the high pressure
evaporator 41.
The steam turbine 14, the high pressure medium turbine 31a, and
the low pressure medium e 31b are coaxially coupled with a tor
37, a generator 38a, and a generator 38b, respectively.
<Condenser/Evaporator> ,
Now, a configuration of the condenser/evaporator 20 will be
described with reference to
The ser/evaporator 20 includes an upper evaporator 60, and
a lower evaporator 61 arranged below the upper evaporator 60. The
condenser/evaporator 20 further es vapor medium communication
pipes 62 and a liquid medium downcomer 72 which connect the upper
evaporator 60 and the lower evaporator 61.
The upper evaporator 60 includes a cylindrical upper evaporator
barrel 63 which s horizontally. Low pressure vapor medium
discharge units 64 are arranged on the top of the upper evaporator barrel 63.
The low pressure vapor medium supply piping 54 is connected to the low
pressure vapor medium discharge units 64. An upper liquid medium
introduction unit 65 branched from the preheater liquid medium outlet
piping 53 ( is connected to an upper portion of the upper evaporator
barrel 63. The upper liquid medium introduction unit 65 is ed into
and arranged in the upper n of the upper ator barrel 63. The
upper liquid medium introduction unit 65 extends horizontally inside the
upper evaporator barrel 63, and has a large number of nozzles 75 which are
horizontally distributed.
In the upper evaporator barrel 63, a plurality of porous plates 66
ing horizontally are arranged in parallel so as to be ally
separated from each other.
The lower evaporator 61 includes a cylindrical loWer evaporator
barrel 67 which extends horizontally in parallel with the upper ator
barrel 63. Lower liquid medium introduction units 68 branched from the
preheater liquid medium outlet piping 53 ( are connected to the
bottom portion of the lewer evaporator barrel 67. The high pressure
medium turbine return piping 52 is connected to an upper portion of the
lower evaporator barrel 67.
A large number of heat transfer pipes 69 are arranged in parallel
with each other in the lower evaporator barrel 67. The heat transfer pipes
69 are U'shaped pipes each having straight pipe portions which extend
horizontally straight and a curved pipe portion which is vertically curved. A
steam turbine return piping connection unit 70 connected to the steam
turbine return piping 15 ( is formed on the lower evaporator barrel 67
on the inlet side of the heat transfer pipes. 69. A condensate/steam
discharge unit 71 connected to the condensate piping 50 and the gas cooler
inlet piping 51 ( is formed on the lower evaporator barrel 67 on the
outlet side of the heat transfer pipes 69. The steam turbinereturn piping
connection unit 70 is located above the condensate/steam discharge unit 71.
The vapor medium ication pipes 62 extend vertically to
make the upper evaporator barrel 63 and the lower evaporator barrel 67
communicate with each other. The vapor medium communication pipes 62
have open top ends which protrude somewhat above the bottom of the upper
evaporator barrel 68. The‘lower ends of the vapor medium communication
pipes 62 are opened to the top of the lower evaporator barrel 67.
The top end of the liquid medium downcomer 72 is opened to the
bottom of the upper ator barrel 63. The lower portion of the liquid
medium downcomer 72 penetrates the upper portion of the lower evaporator
barrel 67. The lower end of the liquid medium mer 72 is opened in
the lower evaporator barrel 67 near the bottom.
Next, an operation of the condenser/evaporator 20 will be
described.
Part of the liquid medium from the preheater liquid medium outlet
piping 53 ( is d into the upper portion of the upper evaporator
barrel 63 through the nozzles 75 of the upper liquid medium introduction
unit 65. The liquid medium falls on the porous plates 66, passes through
the porous plates 66 downward, and is accumulated in the lower n of
the upper evaporator barrel 63 to form an upper evaporator barrel liquid
medium surface 80. The upper ator barrel liquid medium surface 80
is controlled to be positioned below the porous plate 66 that is located the
lowest. The liquid medium in the upper evaporator barrel 63 is further
introduced into the lower ator barrel 67 through the liquid medium
downcomer 72.
Part of the liquid medium from the preheater liquid medium output
piping 53 is introduced into the lower evaporator barrel 67 from the bottom
h the lower liquid medium introduction units 68.
The liquid medium in the lower evaporator barrel 67 forms a lower
evaporator barrel liquid medium surface 81. The lower evaporator barrel
liquid medium surface 81 is controlled to be positioned above the uppermost
portion of the heat transfer pipes 69 and below the portion Where the high
pressure medium turbine return piping 52 is connected to the lower
evaporator barrel 67.
Medium gas having a high degree of superheat, discharged from
the high pressure medium turbine 31a (, is introduced into the upper
portion of the lower evaporator barrel 67 through the high pressure medium
turbine return piping 52.
The steam rged from the steam turbine is introduced into the
heat transfer pipes 69 from the steam turbine return piping 15 (see
through the steam turbine return piping connection unit 70. Note that the
steam contains noncondensable gas. Most of the steam in the heat er
pipes 69 is cooled and condensed by the liquid medium outside the heat
transfer pipes 69. The resultant is discharged from the condensate/steam
discharge unit 71 as a gas-liquid tWo-phase flow, and sent to the condensate
piping 50 and the gas cooler inlet piping 51. In the condensate
piping 50 and the gas cooler inlet piping 51 are shown to be separately
extended from the condenser/evaporator 20. However, as shown in
such piping may be extended from the condenser/evaporator 20 as a single
ser/evaporator discharge unit 71 and may be ed downstream.
In the lower evaporator barrel 67, the liquid medium outside the
—16-
heat transfer pipes 69 is heated to evaporate from the areas in contact with
the heat transfer pipes 69, and rises to above the lower evaporator barrel
liquid medium surface 81 as bubbles. The bubbles are merged with the
vapor medium introduced through the high re medium turbine return
piping 52. The resultant passes through the vapor medium communication
pipes 62 upward and flows into the upper evaporator barrel 63.
In the upper evaporator barrel 63, the rising vapor medium and the
falling liquid medium make direct contact and get mixed with each other for
heat exchange. Eventually, the vapor medium near its saturation
temperature is sent to the low pressure vapor medium supply piping 54
through the low pressure vapor medium discharge units 64.
According to this embodiment, the efficiency of the binary power
generation system combining a geothermal flash steam cycle and a working
medium cycle can be increased.
The low-temperature liquid medium coming out of the regenerator
32 is used as a cold source of the gas cooler 22. The cold heat enables
emission of highly-concentrated noncondensable gas. The liquid medium
can also be heated for a regeneration effect.
In particular, the high-temperature hot water from the first
pressure reducing steam-liquid tor 12 is used to ator the
working medium at higher pressure, and the turbines are driven by the
medium gases of two different pressures. This can increase the generation
output power without increasing the degree of eat at the . In
other words, the temperature levels of the geothermal steam and hot water
can be utilized to reduce the degree of eat.
[THIRD EMBODIMENT],
is a system diagram showing a configuration of a third
embodiment of the binary power generation system according to the present
invention.
This ment is a medification of the second embodiment.
Differences from the second embodiment willbe mainly described here.
In this embodiment, part of the steam is extracted at an
intermediate stage. The extracted steam is sent to the
condenser/evaporator 20 through the steam turbine return piping 15.
- Water steam discharged from the lowest stage of the steam turbine
14 is sent to a ser 91 h steam turbine discharge piping 90.
The condenser 91 is connected with a cold water system 93 including a cold
water pump 92. The cold water system 93 cools the water steam in the
condenser 91 into condensate. The pressure inside the condenser 91 is .
preferably lower than or equal to heric pressure.
As described above, this embodiment differs from the second
embodiment in that the water steam sent to the condenser/evaporator 20
through the steam turbine return piping 15 is extracted steam, and that the
water steam discharged from the lowest stage of the steam turbine 14 is sent
to the condenser 91. The rest of the configuration and operation are the
same as in the second embodiment.
The operation and advantages of the third ment are
basically the same as those of the second embodiment. The third
embodiment is advantageouswhen the flashed steam is large in amount, i.e.,
when the volumetric flow rate of the water steam. discharged from the steam
turbine 14 is high.
[OTHER EMBODIMENTS}
Several embodiments of the t invention have been described
so. far. The foregoing embodiments have been presented by way of example,
and are not intended to limit the scope of the invention. The foregoing
embodiment can be practiced in various other forms, and various omissions,
tutions, and modifications may be made Without departing from the
gist of the invention. Such embodiments and modifications are intended to
be covered by the scope and gist of the invention, as well as embraced in the
inventions set forth in the claims and the range of equivalency thereof.
For example, in the ing embodiments, different generators
are attached to the respective turbines. However, a common generator may
be attached to a plurality of turbines by connecting the shafts of the turbines
to each other or by coupling the shafts via gears.
In the fOregoing second embodiment, horizontally-extending porous
trays may be arranged instead of the porous plates 66 arranged in the upper
evaporator barrel 63.
EXPLANATION OF REFERENCE SYMBOLS
11! rmal heat source water piping
121 first pressure ng steam-liquid separator
131 water steam ing valve
141 steam turbine
153 steam turbine return piping
162 medium superheater
17 3 second pressure reducing steam-liquid separator
181 re reducing valve
191 steam-liquid separator
: condenser/evaporator
211 preheater
221 gas cooler
301 vapor medium governing valve
30a! high pressure vapor medium governing valve
30b3 low pressure vapor medium governing valve
313 medium turbine
81a: high re medium turbine '
31b3 low pressure medium turbine
323 regenerator
333 medium condenser
343 cold water pump
351 cold water system
361 medium pump
373 generator
381 generator
38a! generator
38b: generator
413 high pressure evaporator
423 high pressure preheater
433 branching point
443 medium pressurizing pump
501 condensate piping
513 gas cooler inlet piping
523 high pressure medium turbine return piping
531 preheater liquid medium outlet piping
543 low pressure vapor medium supply piping
602 upper ator
613 lower evaporator
623 vapor medium communication pipe
632 upper evaporator barrel
641 lower pressure vapor medium discharge unit
_20_
_ upper liquid medium introduction unit
66: porous plate
67: lower evaporator barrel
68: lower liquid medium introduction unit
69: heat transferppipe
70: steam turbine return piping connection unit
71: condensate/steam rge unit
72: liquid medium downcomer
75: nozzle
80$ upper evaporator barrel liquid medium surface
81: lower evaporator barrel liquid medium surface
9o: evaporator turbine discharge piping
91: condenser
cold water pump
93: coldwater system
Claims (3)
1. A binary power generation system comprising: a first pressure reducing steam-liquid separator that reduces pressure of geothermal heat source water to separate the geothermal heat source water into water steam and hot liquid water; a steam turbine that is driven by the water steam; a condenser/evaporator that is configured to transfer heat of the water steam discharged from the steam turbine to a liquid medium so that the water steam is condensed and the liquid medium is ated; a medium superheater that transfers heat from the hot liquid water to the evaporated liquid medium to generate a superheated vapor ; a medium turbine that is driven by the superheated vapor medium; a second pressure reducing liquid separator that reduces pressure of the hot liquid water from the medium superheater to separate the hot liquid water into water steam and hot liquid water, wherein the water steam separated by the second pressure reducing steam-liquid separator is led into the condenser/evaporator along with the water steam discharged from the steam turbine; a gas cooler that further cools gas remaining in the condenser/evaporator by using the eated vapor medium discharged from the medium turbine as a cold source, thereby separating and discharging noncondensable gas contained in the gas; and at least one generator to be driven by the steam turbine and the medium turbine.
2. The binary power generation system according to claim 1, r comprising: a medium condenser that cools and condenses the superheated vapor medium discharged from the medium turbine to generate the liquid medium, wherein the gas cooler uses the liquid medium ted by the medium condenser as the cold source.
3. The binary power generation system according to claim 2, further comprising: a regenerator that cools the superheated vapor medium discharged from the medium turbine and transfers heat obtained by cooling the superheated vapor medium to the liquid medium generated by the medium condenser, n the gas cooler uses the liquid medium heated by the regenerator as the cold source.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| NZ715424A NZ715424B2 (en) | 2011-10-03 | 2012-10-03 | Binary power generation system |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011-219123 | 2011-10-03 | ||
| JP2011219123A JP5763495B2 (en) | 2011-10-03 | 2011-10-03 | Binary power generation system |
| PCT/JP2012/006362 WO2013051265A1 (en) | 2011-10-03 | 2012-10-03 | Binary power generation system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| NZ622394A NZ622394A (en) | 2016-05-27 |
| NZ622394B2 true NZ622394B2 (en) | 2016-08-30 |
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