CN110107368A - Steam condensing method, steam and condensate system and electricity generation system - Google Patents
Steam condensing method, steam and condensate system and electricity generation system Download PDFInfo
- Publication number
- CN110107368A CN110107368A CN201910498798.XA CN201910498798A CN110107368A CN 110107368 A CN110107368 A CN 110107368A CN 201910498798 A CN201910498798 A CN 201910498798A CN 110107368 A CN110107368 A CN 110107368A
- Authority
- CN
- China
- Prior art keywords
- cooling medium
- heat exchanger
- transfer process
- high temperature
- heat transfer
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000000034 method Methods 0.000 title claims abstract description 141
- 230000005611 electricity Effects 0.000 title claims abstract description 18
- 239000002826 coolant Substances 0.000 claims abstract description 155
- VNWKTOKETHGBQD-UHFFFAOYSA-N methane Chemical compound C VNWKTOKETHGBQD-UHFFFAOYSA-N 0.000 claims abstract description 147
- 239000003949 liquefied natural gas Substances 0.000 claims abstract description 125
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 118
- 239000007789 gas Substances 0.000 claims abstract description 80
- 239000003345 natural gas Substances 0.000 claims abstract description 74
- 238000010248 power generation Methods 0.000 claims abstract description 13
- 238000007599 discharging Methods 0.000 claims abstract description 11
- 239000012071 phase Substances 0.000 claims description 42
- 238000001816 cooling Methods 0.000 claims description 31
- 239000013535 sea water Substances 0.000 claims description 27
- 239000007791 liquid phase Substances 0.000 claims description 8
- 238000009833 condensation Methods 0.000 description 30
- 230000005494 condensation Effects 0.000 description 29
- 238000002309 gasification Methods 0.000 description 23
- 238000002485 combustion reaction Methods 0.000 description 9
- 239000002918 waste heat Substances 0.000 description 6
- 239000002699 waste material Substances 0.000 description 6
- 238000010586 diagram Methods 0.000 description 5
- 239000013256 coordination polymer Substances 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
- 238000010795 Steam Flooding Methods 0.000 description 2
- 238000010521 absorption reaction Methods 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 239000003245 coal Substances 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 230000017260 vegetative to reproductive phase transition of meristem Effects 0.000 description 2
- CURLTUGMZLYLDI-UHFFFAOYSA-N Carbon dioxide Chemical compound O=C=O CURLTUGMZLYLDI-UHFFFAOYSA-N 0.000 description 1
- 235000011089 carbon dioxide Nutrition 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 238000003912 environmental pollution Methods 0.000 description 1
- 238000007710 freezing Methods 0.000 description 1
- 230000008014 freezing Effects 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 230000021715 photosynthesis, light harvesting Effects 0.000 description 1
- 238000004064 recycling Methods 0.000 description 1
- 238000012827 research and development Methods 0.000 description 1
- 238000000926 separation method Methods 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
- F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
- F01K11/02—Plants characterised by the engines being structurally combined with boilers or condensers the engines being turbines
-
- 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
- F01K19/00—Regenerating or otherwise treating steam exhausted from steam engine plant
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28B—STEAM OR VAPOUR CONDENSERS
- F28B9/00—Auxiliary systems, arrangements, or devices
-
- 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
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
The present invention provides steam condensing method, steam and condensate system and electricity generation system.The high temperature steam discharge that steam condensing method of the invention is used to that power generation turbine to be made to generate is condensed into condensed water, comprising: the first heat transfer process, the high temperature steam discharge discharge thermal energy to the first cooling medium in First Heat Exchanger and form condensed water；Second heat transfer process, second cooling medium directly or indirectly carries out heat exchange with first cooling medium, first cooling medium absorbs the cold energy of second cooling medium in second heat transfer process, at the same time, second cooling medium becomes gas phase natural gas from liquid natural gas by discharging the cold energy, before carrying out first heat transfer process, carries out second heat transfer process, also, the energy of the thermal energy and the cold energy is roughly equal.
Description
Technical field
The present invention relates to application of the LNG cold energy technology in generating set, in particular to utilization LNG cold energy to combustion
The steam that turbine discharge in the generating sets such as coal fired power generating unit, gas-steam combined circulating generation unit is condensed is cold
Solidifying method and the electricity generation system for applying this method.
Background technique
Natural gas is widely used as one of environmentally friendly green energy.Natural gas is largely during transportation
It is conveyed in a manner of liquefied natural gas (LNG).The LNG largely conveyed carries a large amount of cold energy, if cannot be effectively
Utilize these cold energy, it will cause huge energy waste and environmental pollution.Therefore, applicable research and development cold to LNG
It is carrying out always.
Currently, the purposes of LNG cold energy has: power generation, liquefied air separation, warehouse freezing, dry ice processed, low-temperature grinding etc..It is cold
The selection of energy Utilization plan need to be comprehensive point according to many factors such as the techniques, market situation, energy utilization efficiency of LNG receiving station
Analysis.LNG cold energy is used for stirling generator and freezer refrigerating for example, disclosing in patent document 1.
On the other hand, in the known technology using natural gas power, the hair of gas-steam combined circulating generation unit
Electrical efficiency highest, industry, which is generally acknowledged, can reach 50% or so.In other 50% loss, steam Rankine cycle is (solidifying in condenser
Vapour device) in the cold source energy heat taken away by recirculated water, up to 50% or so of entire steam Rankine cycle efficiency.For fire coal
Fired power generating unit generating efficiency is generally 40% hereinafter, 60% or more of entire Rankine cycle efficiency shared by cold source energy, it is seen then that cold
The cooling efficiency (condensation efficiency of steam Rankine cycle) of condenser directly affects the efficiency of steam Rankine cycle, and then influences power generation
The generating efficiency of unit.
Existing technical literature
Patent document 1:CN109339973A
Summary of the invention
The present invention exactly proposes that the first purpose is to provide a kind of benefit in view of above-mentioned problems of the prior art
The steam condensing method that the turbine discharge in gas-steam combined circulating generation unit is condensed with LNG cold energy, thus
It can be improved the condensation efficiency in Rankine cycle, and then improve the generating efficiency of electricity generation system.
It is yet another object of the invention to provide a kind of combined generating systems for applying steam condensing method of the invention.
To achieve the goals above, the present invention adopts the following technical scheme that.
(1) steam condensing method as one of mode of the present invention, the high temperature steam discharge for generating power generation turbine
It is condensed into condensed water, which is characterized in that including following heat transfer process:
First heat transfer process, the high temperature steam discharge discharge thermal energy to the first cooling medium in First Heat Exchanger and form condensation
Water；
Second heat transfer process, the second cooling medium directly or indirectly carry out heat exchange, institute with first cooling medium
It states the first cooling medium and absorbs the cold energy of second cooling medium in second heat transfer process, it is at the same time, described
Second cooling medium becomes gas phase natural gas from liquid natural gas by discharging the cold energy,
Before carrying out first heat transfer process, carry out second heat transfer process, also, the thermal energy with it is described cold
The energy of energy is roughly equal.
(2) in the steam condensing method described in (1), second heat transfer process can also be replaced, and be arranged with it is described
The parallel third heat transfer process of first heat transfer process,
In first heat transfer process, a part of the high temperature steam discharge is cold in the First Heat Exchanger and described first
But medium carries out heat exchange and forms the first condensed water；
In the third heat transfer process, the rest part of the high temperature steam discharge is in third heat exchanger to the second cooling medium
It discharges thermal energy and forms the second condensed water, at the same time, second cooling medium is by discharging cold energy from the liquid phase day
Right gas becomes the gas phase natural gas；
The thermal energy and described second that the rest part of the high temperature steam discharge discharges in the third heat transfer process are cold
But the amount for the cold energy that medium discharges in the third heat transfer process is equal；
The process that the method also includes making first condensed water and second condensed water converge.
(3) in the steam condensing method described in (1), it can also also set up and exchange heat with first heat transfer process and second
The third heat transfer process of concurrent process,
In first heat transfer process, a part of the high temperature steam discharge is cold to described first in the First Heat Exchanger
But medium discharges thermal energy and forms the first condensed water；
In the third heat transfer process, the rest part of the high temperature steam discharge is in third heat exchanger to the second cooling medium
It discharges thermal energy and forms the second condensed water, at the same time, second cooling medium is by discharging cold energy from liquid natural gas
Become gas phase natural gas；
The thermal energy and the high temperature steam discharge that described a part of the high-temperature gas discharges in first heat transfer process
The sum of the amount of thermal energy that is discharged in the third heat transfer process of the rest part, with second cooling medium described
The sum of the amount of cold energy discharged in second heat transfer process and the third heat transfer process is equal；
The process that the method also includes making first condensed water and second condensed water converge.
(4) in above-mentioned steam condensing method, when first cooling medium is recirculated water,
First cooling medium to have heated up in first heat transfer process through heat exchange is in second heat exchange
Directly or indirectly heat exchange is carried out with second cooling medium in the process and is cooled down,
Desuperheated first cooling medium is back to the First Heat Exchanger in second heat transfer process, in institute
It states in the first heat transfer process and carries out heat exchange with the high temperature steam discharge.
It (5) is the Lake Water not being recycled, rivers in first cooling medium in above-mentioned steam condensing method
When water or seawater,
Cool down in second heat transfer process through heat exchange from external first cooling medium, the cooling
First cooling medium be directed to the First Heat Exchanger and carry out heat exchange with the high temperature steam discharge, described first
First cooling medium that heat exchanger has heated up through heat exchange is discharged to the outside.
(6) in above-mentioned steam condensing method, it is also possible that described second is cooling in second heat transfer process
The cold energy is passed to air by medium, and the air and first cooling medium for absorbing the cold energy carry out hot friendship
It changes, so that first cooling medium absorbs the cold energy.
(7) steam and condensate system as another mode of the invention, the high temperature steam discharge for generating power generation turbine are cold
It congeals into condensed water and collects characterized by comprising
First Heat Exchanger makes the high temperature steam discharge form condensed water to the first cooling medium release thermal energy and collects；
Second heat exchanger makes first cooling medium and the second cooling medium directly carry out heat exchange, and described first is cold
But the cold energy of the second cooling medium described in Absorption of Medium, at the same time, second cooling medium is by discharging the cold energy
Become gas phase natural gas from liquid natural gas, also, the energy of the thermal energy and the cold energy is roughly equal；
High-temperature gas flow path is connect with the First Heat Exchanger, and the high temperature steam discharge is guided to the First Heat Exchanger；
First medium flow path makes the first cooling medium followed by second heat exchanger, the First Heat Exchanger；With
Second medium flow path makes second cooling medium flow through second heat exchanger.
(8) in above-mentioned steam and condensate system, the first medium flow path can be circulation stream, can also be and does not follow
Circulation road,
If the first medium flow path is circulation stream, first cooling medium is followed by second heat exchange
Second heat exchanger is back to after device and the First Heat Exchanger；
If the first medium flow path is that circulation stream, first cooling medium from outside are not flowing successively
After second heat exchanger and the First Heat Exchanger and guide to outside.
It (9) may include multiple second heat exchangers, each second heat exchanger in above-mentioned steam and condensate system
Include the input terminal and output end of the second cooling medium, enters described the second of second heat exchanger from the input terminal
Cooling medium flows out after heat exchange discharges cold energy from the output end,
At least two in multiple second heat exchangers connect in parallel or serial fashion,
The first medium flow path includes the first medium branch of multiple parallel connections, and each first medium branch is respectively by institute
The first cooling medium is stated to guide to each second heat exchanger；
The cold energy that the amount of the thermal energy and second cooling medium discharge in each second heat exchanger
The sum of amount is equal.
(10) steam and condensate system of the invention can also be such as flowering structure, comprising:
First Heat Exchanger makes the high temperature steam discharge discharge thermal energy to the first cooling medium and form condensed water；
Second heat exchanger makes air and the second cooling medium carry out heat exchange, so that the air be made to absorb described second
The cold energy of cooling medium, at the same time, second cooling medium is by discharging the cold energy from the liquid phase day of the first temperature
Right gas becomes the gas phase natural gas of second temperature, also, the energy of the thermal energy and the cold energy is roughly equal；
Air-cooling apparatus makes first cooling medium carry out heat exchange with the air for absorbing the cold energy,
To make first cooling medium absorb the cold energy；
High-temperature gas flow path is connect with the First Heat Exchanger, and the high temperature steam discharge is guided to the First Heat Exchanger；
First medium flow path makes the first cooling medium followed by the air-cooling apparatus, the First Heat Exchanger；
Air flow circuit makes the air flow successively through second heat exchanger, the air-cooling apparatus；With
Second medium flow path makes second cooling medium flow through second heat exchanger.
(11) steam and condensate system of the invention can also be such as flowering structure, comprising:
First Heat Exchanger makes a part of the high temperature steam discharge and the first cooling medium carry out heat exchange and form first and coagulate
It bears water and collects；
Third heat exchanger makes the rest part of the high temperature steam discharge discharge thermal energy to the second cooling medium and form second and coagulate
It bears water and collects, at the same time, second cooling medium is become by release cold energy from the liquid natural gas of the first temperature
Second stable gas phase natural gas, the thermal energy of the rest part release of the high temperature steam discharge and second cooling Jie
The amount of the cold energy of matter release is equal；
First high-temperature gas flow path, is connected to the First Heat Exchanger, by a part guidance of the high-temperature gas to institute
State First Heat Exchanger；
Second high-temperature gas flow path is connected to the third heat exchanger, by the rest part of the high-temperature gas guide to
The third heat exchanger；
Wherein, second condensed water converges via pipeline with first condensed water.
(12) electricity generation system as another mode of the invention, comprising: generator；The generator is driven to generate electricity
And the steam turbine of high temperature steam discharge is discharged；And steam and condensate system described in any one of above-mentioned (7) to (11).
Invention effect
Through the invention, it at least can be realized following technical effect.
1) fossil-fired unit, the cold source energy in gas-steam combined generating set is made full use of to heat LNG gasification
Or promote natural gas temperature.
2) turbine discharge temperature, pressure in generating set are reduced, the generating efficiency of Rankine cycle power generation etc. is increased.
3) fossil-fired unit is avoided, the Negative environment shadow that combined cycle generating unit cold source energy causes seawater to heat up
It rings.
4) original LNG gasification or cold energy generation refrigerated sea water are avoided, the negative environmental consequences such as ocean temperature decline are caused.
5) fossil-fired unit or the thermal energy and LNG gasification mistake of fuel gas-steam electricity generation system high temperature steam discharge are utilized simultaneously
The cold energy discharged in journey, and the thermal energy is matched with cold energy, so as to improve condensing engine condensation efficiency and then improving
While the cycle efficieny of Rankine cycle, the energy is made full use of, avoids the waste of energy.
Detailed description of the invention
Fig. 1 is the structural schematic diagram using the electricity generation system of the steam and condensate system of the embodiment of the present invention 1.
Fig. 2 is the structural schematic diagram using the electricity generation system of the steam and condensate system of the embodiment of the present invention 2.
Fig. 3 is the structural schematic diagram using the electricity generation system of the steam and condensate system of the embodiment of the present invention 3.
Fig. 4 is the structural schematic diagram using the electricity generation system of the steam and condensate system of the embodiment of the present invention 4.
Fig. 5 is the structural schematic diagram using the electricity generation system of the steam and condensate system of the embodiment of the present invention 5.
Description of symbols
1- gas turbine；The combustion chamber 2-；3- compressor；4- waste heat boiler；6- condensate pump；7- low-pressure heater；8- high
Press heater；9- feed pump；11-LNG storage tank；12,13- heaters (the second heat exchanger)；14- expanding machine；15- natural gas transportation
Pipeline；21- steam turbine；22- condenser (First Heat Exchanger)；23- valve；The first exhaust stream of 24- road；The second exhaust stream of 25- road；
25a, 25b- steam discharge branch flow passage；26- condensed water flow path；26a, 26b- condensed water branch；27- hot well (condensation water collection dress
It sets)；28- seawater/recirculated water flow path (the first cooling medium flow path)；(first is cooling for 28a, 28b- seawater/recirculated water branch flow passage
Medium branch flow passage)；29- low temperature seawater/recirculated water flow path (the first cooling medium flow path)；29a, 29b- low temperature seawater/circulation
Water branch (the first cooling medium branch)；30- condensed water conveyance conduit；40- Air-Cooling Island (air-cooling apparatus)；41a, 41b- heat
Air branch flow passage；42a, 42b- cold air branch；50- cold energy stirling generator；50a- cold end；The hot end 50b-；G- power generation
Machine, HG- high temperature steam discharge.
Specific embodiment
Referring to Fig. 1 to Fig. 5, specific embodiments of the present invention will be described in detail.In attached drawing, for identical
Component or part mark identical appended drawing reference, and omit to its repeated explanation.
It is to return the high-temperature gas of gas turbine discharge as one of generation mode in gas-steam combined power plant
It receives into waste heat boiler, the water supply in steam generating system is heated to generate steam, using the steam drive steam turbine,
The further driven generator power generation of steam turbine.Steam turbine can generate a large amount of high temperature steam discharge (steam) at work, therefore, in vapour
The exhaust steam end of turbine is connected with steam and condensate system, for recycling high temperature steam discharge and being transmitted back in the form of condensed water steam-electric power
The water supply system of system.
When condensing high temperature steam discharge, the present invention takes full advantage of liquefied natural gas (LNG) and contains a large amount of cold energy
Feature uses liquefied natural gas (LNG) as cooling medium when condensation, and maximum utilize of energy is sought (to could also say that
The least disadvantage of energy).
In the following, being illustrated in conjunction with attached drawing to each embodiment of steam condensing method of the invention.
First embodiment
As shown in Figures 1 to 4, combined cycle generation system of fuel gas-steam includes gas turbine 1, combustion chamber 2, compressor
3, waste heat boiler 4, steam turbine 21.Heated natural gas from natural gas line 15 enters the combustion chamber 2 of gas turbine,
The pressure-air being pressed into compressor 3 mixes, and drives gas turbine 1.The high-temperature gas that gas turbine 1 generates enters waste heat boiler
4, water is heated into the steam of high temperature and pressure.The steam drive steam turbine 21 rotation, individually or together with above-mentioned gas turbine
Driven generator G power generation.
It further include the steam that the high temperature steam discharge that above-mentioned steam turbine 21 is discharged is condensed into condensed water in the electricity generation system
Condenser system.The steam and condensate system includes condenser 22, and condenser 22 is connected to the exhaust steam end of steam turbine 21 to receive steamer
The high temperature steam discharge HG of machine 21.The condenser 22 mainly includes the row flowed for high temperature steam discharge HG and connect with condensation water collecting device
Steam flow road and cooling cooling medium flow path is carried out to high temperature steam discharge HG.As it can be seen that condenser 22 is a kind of heat exchanger (also referred to as
One heat exchanger).
As the cooling medium (also referred to as the first cooling medium) for participating in heat exchange in condenser 22, generally use recyclable
The recirculated water used or the seawater not being recycled.
In order to improve the condensing efficiency of condenser 22, in the present embodiment, make recirculated water used in condenser 22 or
The cooling mediums such as seawater first carry out heat exchange with the cooling medium (also referred to as the second cooling medium) of more low temperature, then again with condenser
High temperature steam discharge HG in 22 carries out heat exchange.In detail, it in the heat exchanger (the second heat exchanger) other than condenser 22, utilizes
Second cooling medium and the first cooling medium directly or indirectly carry out heat exchange, and the first cooling medium is made to cool down, desuperheated
First cooling medium is directed to condenser 22, carries out the condensation of high temperature steam discharge HG with higher efficiency.
It on the other hand, is with low temperature (the first temperature) liquid in transport as the liquefied natural gas LNG of the second cooling medium
The form of state, such as temperature can need to be heated to form predetermined temperature (second before it will send to combustion chamber 2 down to -162 DEG C
Temperature, also referred to as feed air temperature) gas phase, it is therefore desirable to absorb thermal energy (or release cold energy).
In the present invention, in the cold energy using liquefied natural gas LNG to recirculated water, not recirculated water (such as Lake Water, rivers
Water, seawater) etc. the first cooling medium while cooled down, also assign heat to liquefied natural gas LNG using the first cooling medium
It can be allowed to become gas phase from liquid phase.When the cold energy that the gas phase natural gas that liquefied natural gas LNG becomes predetermined temperature is discharged (is inhaled
The thermal energy of receipts) with high temperature steam discharge HG become cold energy (thermal energy discharged) that condensed water is absorbed it is equal when, not only increase solidifying
The condensation efficiency of vapour device 22, also achieves thermal energy and the maximum of cold energy utilizes.In the situation for not considering energy dissipation etc. in pipeline
Under, the not waste of energy.It should be noted that phase-state change can be only existed after liquefied natural gas becomes gas phase natural gas
Without temperature change, can also not only there be phase-state change but also there are temperature changes.
If being indicated with energy balance formula, there are following relationships.
QAlways=FLNG*QLNG gasification latent heat+FLNG*(TFor-T0)*CpGas=QTurbine discharge
Wherein, QAlwaysIndicate the total amount for the cold energy that the liquefied natural gas for turbine discharge condensation is discharged；QTurbine dischargeTable
Show that turbine discharge is condensed into the total amount for the thermal energy that condensed water is discharged；FLNGIndicate the liquefaction day for turbine discharge condensation
Right gas total flow；QLNG gasification latent heatIndicate the gasification latent heat of the liquefied natural gas of unit volume；T0Indicate the first above-mentioned temperature；TFor
Indicate above-mentioned second temperature (feed air temperature)；CpGasIndicate the avergae specific heat of gas phase natural gas.
In conclusion the first embodiment of steam condensing method of the invention includes the first heat transfer process and the second heat exchange
Process.
In the first heat transfer process, the high temperature steam discharge of steam turbine discharge thermal energy to the first cooling medium in First Heat Exchanger and
Form condensed water.
In the second heat transfer process, the second cooling medium directly or indirectly carries out heat exchange with the first cooling medium, the
One cooling medium absorbs the cold energy of the second cooling medium in the second heat transfer process, and at the same time, the second cooling medium passes through
It discharges the cold energy and becomes the gas phase natural gas of second temperature from the liquid natural gas of the first temperature.Herein, the first temperature system
The initial temperature (such as from temperature when LNG storage tank outflow, but initial temperature is certainly not limited to this) of liquid natural gas, second
Temperature system will send to the feed air temperature of combustion chamber of gas turbine.
Before carrying out the first above-mentioned heat transfer process, the second above-mentioned heat transfer process, also, the high temperature of steam turbine are carried out
The amount of the thermal energy that steam discharge discharges in the first heat transfer process and the cold energy that the second cooling medium discharges in the second heat transfer process is big
It causes equal.
It is so-called herein " roughly equal ", it is because it is contemplated that terminating to terminate this to the first heat transfer process from the second heat transfer process
Period issuable cold energy scatters and disappears, and is not considering energy refrigerating loss ideally, the amount phase of above-mentioned thermal energy and above-mentioned cold energy
Deng means that: the cold energy that liquefied natural gas discharges in above-mentioned second heat transfer process is all used for the condensation of turbine discharge, and
The amount of the cold energy is just the amount of cold energy needed for turbine discharge condenses.
Second embodiment
In the first embodiment, condenser 22 is connected to the exhaust steam end of steam turbine 21, receives all high of steam turbine 21
Warm steam discharge HG；But in the present embodiment, the exhaust steam end of steam turbine 21 is branched off into the first exhaust line 24 and the second exhaust line
25 two high temperature steam discharge flow paths.A part of high temperature steam discharge HG flows into condenser 22 via the first exhaust line 24, by seawater,
First cooling medium such as recirculated water is cooled down.The rest part of high temperature steam discharge HG flows into condensing via the second exhaust line 25
In condenser (also referred to as third heat exchanger) other than device 22.
In the third heat exchanger, high temperature steam discharge is set to be condensed into condensed water using the cold energy of liquefied natural gas LNG.It is utilizing
While the cold energy of liquefied natural gas LNG condenses the high temperature steam discharge that the conveying of the second exhaust line 25 comes, the portion is also utilized
Divide high temperature steam discharge to carry out heating to liquefied natural gas LNG to be allowed to become gas phase from liquid phase.When initial temperature (the first temperature, such as-
162 DEG C) liquefied natural gas LNG become the cold energy that the gas phase natural gas of predetermined temperature (second temperature, feed air temperature) is discharged
The high temperature steam discharge HG that (thermal energy absorbed) comes with the conveying of the second exhaust line 25 becomes the cold energy that condensed water is absorbed and (is discharged
Thermal energy) it is equal when, realize the maximum of thermal energy and cold energy and utilize.In the case where not considering energy loss in pipeline, do not have
The waste of energy.
If being indicated with energy balance formula, there are following relationships.
QAlways=FLNG*QLNG gasification latent heat+FLNG*(TFor-T0)*CpGas=QThe steam discharge of second exhaust line
Wherein, QAlwaysIndicate the total amount for the cold energy that the liquefied natural gas for turbine discharge condensation is discharged；
QThe steam discharge of second exhaust lineIndicate the total amount that the thermal energy that condensed water is discharged is condensed by the turbine discharge that the second exhaust line 25 conveys；
FLNGIndicate the liquefied natural gas total flow for turbine discharge condensation；QLNG gasification latent heatIndicate the liquefied natural gas of unit volume
Gasification latent heat；T0Indicate the first above-mentioned temperature；TForIndicate above-mentioned second temperature (feed air temperature)；CpGasIndicate that gas phase is natural
The avergae specific heat of gas.
In conclusion the second embodiment of steam condensing method of the invention includes that the first heat transfer process and third exchange heat
Process.
In the first heat transfer process, a part of high temperature steam discharge carries out heat exchange in First Heat Exchanger and the first cooling medium
And form the first condensed water.
In third heat transfer process, the rest part of high temperature steam discharge discharges thermal energy to the second cooling medium in third heat exchanger
And the second condensed water is formed, at the same time, the second cooling medium is become by release cold energy from the liquid natural gas of the first temperature
At the gas phase natural gas of second temperature.
The first above-mentioned heat transfer process carries out parallel with above-mentioned third heat transfer process, also, its remaining part of high temperature steam discharge
Divide the thermal energy discharged in third heat transfer process equal with the amount for the cold energy that the second cooling medium discharges in third heat transfer process.
The above method further includes the process for making the first condensed water and the second condensed water converge.
Above-mentioned thermal energy is equal with the amount of above-mentioned cold energy means that: liquefied natural gas discharges cold in above-mentioned third heat transfer process
The condensation of the turbine discharge of the second exhaust stream road conveying can be all used for, and the amount of the cold energy is just the second exhaust stream road
The amount of cold energy needed for the turbine discharge of conveying condenses.
Third embodiment
Present embodiment system combines first embodiment with second embodiment and the scheme that is formed.
That is: the steam condensing method of present embodiment includes the first, second, third heat transfer process, wherein is carrying out first
The second heat transfer process is carried out before heat transfer process, third heat transfer process is concurrently carried out with the first heat transfer process.
In the first heat transfer process, a part of high temperature steam discharge discharge thermal energy to the first cooling medium in First Heat Exchanger and
Form the first condensed water.
In the second heat transfer process, the second cooling medium directly or indirectly carries out heat exchange with the first cooling medium, the
One cooling medium absorbs the cold energy of the second cooling medium in the second heat transfer process, and at the same time, the second cooling medium passes through
It discharges the cold energy and becomes the gas phase natural gas of second temperature from the liquid natural gas of the first temperature.Herein, the first temperature system liquid
The initial temperature (such as from temperature when LNG storage tank outflow, but initial temperature is certainly not limited to this) of phase natural gas, the second temperature
Degree system will send to the feed air temperature of combustion chamber of gas turbine.
In third heat transfer process, the rest part of high temperature steam discharge discharges thermal energy to the second cooling medium in third heat exchanger
And the second condensed water is formed, at the same time, the second cooling medium is become by release cold energy from the liquid natural gas of the first temperature
At the gas phase natural gas of the second temperature.
The rest part of thermal energy and high temperature steam discharge that a part of high-temperature gas discharges in the first heat transfer process is in third
The sum of amount of thermal energy discharged in heat transfer process discharges in the second heat transfer process and third heat transfer process with the second cooling medium
The sum of the amount of cold energy it is equal.
This method further includes the process for making the first condensed water and the second condensed water converge.
If being indicated with energy balance formula, there are following relationships.
QAlways=FLNG*QLNG gasification latent heat+FLNG*(TFor-T0)*CpGas=QSecond heat transfer process+QThird heat transfer process=QThe steam discharge of first exhaust line+
QThe steam discharge of second exhaust line
Wherein, QAlwaysIndicate the total amount for the cold energy that the liquefied natural gas for turbine discharge condensation is discharged, this embodiment party
In formula, for the sum of the amount of cold energy discharged in the second heat transfer process and third heat transfer process, i.e. QFirst heat transfer process+QSecond heat transfer process；
QThe steam discharge of first exhaust lineIndicate the amount that the thermal energy that condensed water is discharged is condensed by the turbine discharge that the first exhaust line conveys；
QThe steam discharge of second exhaust lineIndicate the amount that the thermal energy that condensed water is discharged is condensed by the turbine discharge that the second exhaust line conveys；FLNG
Indicate the liquefied natural gas total flow for turbine discharge condensation；QLNG gasification latent heatIndicate the gas of the liquefied natural gas of unit volume
Change latent heat；T0Indicate the first above-mentioned temperature；TForIndicate above-mentioned second temperature (feed air temperature)；CpGasIndicate gas phase natural gas
Avergae specific heat.
In the following, in conjunction with each embodiment illustrate using above embodiment steam condensing method steam and condensate system and
Electricity generation system.
Embodiment 1
As shown in Figure 1, the high temperature exhaust steam end of steam turbine 21 is connected to a port of triple valve 23；The second end of triple valve
Mouth is connected to condenser 22 via the first exhaust stream road 24.The condenser 22 using from external seawater or recirculated water as
Cooling medium (the first cooling medium) makes the high temperature steam discharge come from the conveying of the first exhaust stream road 24 be condensed into condensed water.
The third port of triple valve 23 is connected to the second exhaust stream road 25.Second exhaust stream road 25 is branched off into two steam discharge branches
25a,25b.Steam discharge branch 25a is connected to secondary heater 13, and the high temperature steam discharge flowed through in steam discharge branch 25a adds as second
The heat source of hot device 13.Steam discharge branch 25b is connected to primary heater 12, the high temperature steam discharge conduct flowed through in steam discharge branch 25b
The heat source of primary heater 12.
High temperature steam discharge in steam discharge branch 25a, steam discharge branch 25b discharges in secondary heater 13, primary heater 12
Thermal energy and become condensed water, come together in condensed water flow path 26 via condensed water branch 26a, 26b respectively.The condensed water flow path 26
It is connected to the hot well 27 for collecting condensed water.The hot well 27 is coagulated what is be collected by the high temperature steam discharge in the first exhaust stream road 24
First condensed water made of knot and the second condensed water interflow sent by condensed water flow path 26, and be recycled to via water pump etc.
The water supply system of waste heat boiler, for being recycled next time.
Primary heater 12 and secondary heater 13 are cooled down using the thermal energy of above-mentioned high temperature steam discharge to as the present invention second
The liquefied natural gas of medium is heated, and the low temperature input terminal (or liquid phase input terminal) and high temperature output end of natural gas are all had
(or gas phase input terminal).So-called herein " low temperature " and " high temperature " refer to, by temperature of the natural gas when that will flow into a heater
Degree is known as " high-temperature natural gas " compared with temperature when just flowing out the heater, by the higher side of temperature, and temperature is lower
A side be known as " cryogenic natural gas "；For each heater, there are respective low temperature input terminal and high temperature output end.Similarly,
Sometimes output end is known as by the variation that phase only occurs for heater at this point, input terminal is known as liquid phase input terminal by natural gas
Gas phase outlet.Input terminal is equal with the possible temperature of the natural gas of output end, it is also possible to temperature etc., as long as natural gas is by adding
Hot device releases cold energy.In the present embodiment, the record of " low temperature input terminal " " high temperature output end " is used for ease of understanding
Mode, but this not indicates input terminal and output end is not liquid phase input terminal and gas phase outlet.
By primary heater 12 with secondary heater 13 with the low temperature input terminal phase of the high temperature output end of a side and another party
The mode of connection is connected in series in natural-gas transfer pipeline.More specifically, -162 DEG C of liquefied natural gas LNG is via natural gas
The 15a Duan Ercong LNG storage tank 11 of conveyance conduit is transported to the low temperature input terminal of primary heater 12.The height of primary heater 12
Warm output end is connected to the inlet end of expanding machine 14 via the 15b section of natural-gas transfer pipeline.It heated through primary heater 12
Gasification natural gas as expanding machine 14 internal working medium participation expanding machine 14 work.The natural gas that gasifies is sharp in expanding machine 14
Export mechanical work outward with the expansion of compressed gas decompression with driven generator, and gas carry out being insulated in expanding machine it is swollen
The interior energy of gas itself, therefore the natural gas being discharged from the exhaust outlet of expanding machine 14 and entrance are consumed while swollen external acting
Natural gas when expanding machine 14, which is compared, to be cooled down.From expanding machine 14 be discharged natural gas via natural-gas transfer pipeline 15c section
And it is sent to secondary heater 13.Secondary heater 13 is and defeated through natural gas by the heated by natural gas to defined feed air temperature
It send the 15d section of pipeline and is sent with defined flow to the combustion with the above-mentioned steam turbine 21 together gas turbine of driven generator G
Burn room.
In the present embodiment in such a way that two heaters are connected in series, but a heater can also be only set,
As long as the gas phase natural gas being discharged from output end meets the temperature supplied to combustion chamber of gas turbine after the heater heat exchange
It is required that.Certainly, if after one or two heater, the temperature of gas phase natural gas is not up to air supply requirement (such as 29 DEG C),
Can then connect more heat exchangers, and natural gas is made to continue to heat up to reach the externally temperature requirement for natural gas.
If using QAlwaysIndicate total amount, the Q of the cold energy that the liquefied natural gas for turbine discharge condensation is dischargedThe steam discharge of second exhaust line
It indicates to be condensed into the total amount for the thermal energy that condensed water is discharged, Q1 expression by the turbine discharge that the second exhaust line 25 conveys naturally
Cold energy that gas is discharged in primary heater 12, Q2 indicate cold energy, F that natural gas is discharged in secondary heater 13LNGIt indicates to use
Liquefied natural gas total flow, Q in turbine discharge condensationLNG gasification latent heatThe gasification latent heat of the liquefied natural gas of expression unit volume,
T0Initial temperature, T when expression liquefied natural gas is condensed for steamForIndicate above-mentioned feed air temperature, CpGasIndicate that gas phase is natural
Then there is following equilibrium relation in the avergae specific heat of gas:
QAlways=FLNG*QLNG gasification latent heat+FLNG*(TFor-T0)*CpGas=Q1+Q2=QThe steam discharge of second exhaust line
As described above, be illustrated by taking heater 12,13 there are two having as an example, but the quantity of heater is not limited to
It 2, can be set as needed as more.If indicating the quantity of the heater of participation high temperature steam discharge condensation with n:
QAlways=FLNG*QLNG gasification latent heat+FLNG*(TFor-T0)*CpGas=Q1+Q2+ ...+Qn=QThe steam discharge of second exhaust line
Embodiment 2
As shown in Fig. 2, the high temperature exhaust steam end of steam turbine 21 is connected to condenser 22, by whole high temperature steam discharges supply to
Condenser 22.The condenser 22 makes as cooling medium (the first cooling medium) from defeated using from external seawater or recirculated water
The high temperature steam discharge sent is condensed into condensed water.The hot well 27 of condenser 22 is passed to waste heat pot for collecting the condensed water
The water supply system of furnace.
It is illustrated below using seawater as the example of the first cooling medium.
The seawater (such as 29 DEG C) being introduced from outside into enters secondary heater through seawater branch flow passage 28a, 28b respectively
13, primary heater 12, the heat source of heat source and primary heater 12 respectively as secondary heater 13.
Primary heater 12 and secondary heater 13 are using the thermal energy of above-mentioned seawater to as the second cooling medium of the invention
Liquefied natural gas heated.The flow path of liquefied natural gas in the present embodiment and with primary heater 12 and second heat
The connection of device 13, same as Example 1, repeated description is omitted here.
It has passed through the liquefaction day of the Absorption by Sea Water of primary heater 12, secondary heater 13 initial temperature (the first temperature)
Right gas becomes the cold energy discharged when the gas phase natural gas of defined feed air temperature (second temperature), and carry this these cold energy via
Branch 29a, 29b converge at the first cooling medium flow path 29, and are supplied to condenser 22, with the high temperature steam discharge in condenser 22
HG carries out heat exchange.The seawater that have passed through heat exchange and flow out is, for example, 29 DEG C.It is outer that these seawater can be discharged to ocean etc.
Portion can't impact temperature of the ocean etc..
As described above, being illustrated by taking seawater as an example.Recirculated water also can be used in first cooling medium certainly.It is extra large with using
Water the difference is that, recirculated water can't be discharged to outside after condenser 22 has carried out heat exchange, but again
It is supplied to the first, second heater 12,13, is re-used for absorbing natural gas cold energy.
If using QAlwaysIndicate total amount, the Q of the cold energy that the liquefied natural gas for turbine discharge condensation is dischargedSeawaterIndicate sea
The amount for the cold energy that water absorbs, QRecirculated waterIndicate that the amount for the cold energy that recirculated water absorbs, Q1 indicate that natural gas is released in primary heater 12
Cold energy, the Q2 put indicate cold energy, F that natural gas is discharged in secondary heater 13LNGIndicate the liquid for turbine discharge condensation
Change natural gas total flow, QLNG gasification latent heatIndicate gasification latent heat, the T of the liquefied natural gas of unit volume0Indicate that liquefied natural gas is used for
Initial temperature, T when steam condensesForIndicate above-mentioned feed air temperature, CpGasThe avergae specific heat for indicating gas phase natural gas, then exist
Following equilibrium relation:
QAlways=FLNG*QLNG gasification latent heat+FLNG*(TFor-T0)*CP gas=QSeawater=QRecirculated water=Q1+Q2.
As described above, be illustrated by taking heater 12,13 there are two having as an example, but the quantity of heater is not limited to
It 2, can be set as needed as more.If indicating the quantity of the heater of participation high temperature steam discharge condensation with n:
QAlways=Q1+Q2+…+Qn。
The characteristics of the present embodiment, is that the thermal energy and liquefied natural gas for discharging high temperature steam discharge when condensing become predetermined temperature
Gas phase natural gas when the cold energy that is discharged it is equal, and the cold energy is transmitted using the first cooling medium, so as to avoid energy
Additional demand or waste.Moreover, because the first cooling medium has been assigned cold energy first, so improving the cold of condenser 22
Solidifying efficiency.
Embodiment 3
As shown in figure 3, the difference of the present embodiment and embodiment 2 is only that and has installed Air-Cooling Island 40 additional.It that is: is not embodiment 2
The cold energy of natural gas release is directly absorbed in the first, second heater 12,13 by the first cooling medium like that, but is existed by air
After first, second heater 12,13 absorbs the cold energy of natural gas release, the cold energy is passed into the first cooling in Air-Cooling Island 40
Medium, carrying the cold energy by the first cooling medium condenses the high temperature steam discharge in condenser 22.
In the following, using using recirculated water as illustrating the present embodiment for the first cooling medium.For same as Example 2
Structure, mark identical appended drawing reference and omit the description.
Air from Air-Cooling Island 40 enters secondary heater 13, first through hot-air branch flow passage 41a, 41b respectively
Heater 12, the heat source of heat source and primary heater 12 respectively as secondary heater 13.
Primary heater 12 and secondary heater 13 are situated between using the thermal energy of above-mentioned hot-air to as the second cooling of the present invention
The liquefied natural gas of matter is heated.The flow path of liquefied natural gas in the present embodiment and with primary heater 12 and second plus
The connection of hot device 13, identical as embodiment 1, embodiment 2, repeated description is omitted here.
It has passed through primary heater 12, the air of secondary heater 13 absorbs the liquefaction day of initial temperature (the first temperature)
Right gas becomes the cold energy discharged when the gas phase natural gas of defined feed air temperature (second temperature), and carry these cold energy via
Cold air branch flow passage 42a, 42b enter Air-Cooling Island 40, carry out heat exchange in Air-Cooling Island 40 and the first cooling medium.
Herein, the first cooling medium in Air-Cooling Island is, for example, 29 DEG C of recirculated water.Carry the cold air warp of above-mentioned cold energy
Heat exchange is carried out with the recirculated water and cold energy is all forwarded to recirculated water.The recirculated water is supplied to through recirculated water flow path 29
Condenser 22 makes high temperature steam discharge be condensed into condensed water.Also, as previously mentioned, the liquefied natural gas of initial temperature (the first temperature)
Become the cold energy discharged when the gas phase natural gas of defined feed air temperature (second temperature) and the high temperature steam discharge in condenser 22
In to be condensed into the thermal energy that condensed water is discharged equal.
If using QAlwaysIndicate total amount, the Q of the cold energy that the liquefied natural gas for turbine discharge condensation is dischargedSeawaterIndicate sea
The amount for the cold energy that water absorbs, QRecirculated waterIndicate amount, the Q of the cold energy that recirculated water absorbsIt is air-cooledIndicate the cold energy that air-cooled air absorbs amount,
It is cold that Q1 indicates that cold energy, the Q2 that natural gas is discharged in primary heater 12 indicate that natural gas is discharged in secondary heater 13
Energy, FLNGIndicate the liquefied natural gas total flow for turbine discharge condensation, QLNG gasification latent heatIndicate that the liquefaction of unit volume is natural
Gasification latent heat, the T of gas0Initial temperature, T when expression liquefied natural gas is condensed for steamForIndicate above-mentioned feed air temperature,
CpGas, then there is following equilibrium relation in the avergae specific heat for indicating gas phase natural gas:
QAlways=FLNG*QLNG gasification latent heat+FLNG*(TFor-T0)*CP gas=QSeawater=QRecirculated water=QAir-cooled=Q1+Q2。
As described above, be illustrated by taking heater 12,13 there are two having as an example, but the quantity of heater is not limited to
It 2, can be set as needed as more.If indicating the quantity of the heater of participation high temperature steam discharge condensation with n:
QAlways=Q1+Q2+…+Qn。
The characteristics of the present embodiment, is that the thermal energy and liquefied natural gas for discharging high temperature steam discharge when condensing become predetermined temperature
Gas phase natural gas when the cold energy that is discharged it is equal, and it is cold using the first cooling medium and as the air of intermediate medium to transmit this
Can, so as to avoid the additional demand or waste of energy.Moreover, because the first cooling medium has been assigned cold energy first, institute
To improve the condensation efficiency of condenser 22.
Embodiment 4
As described in mountain, in embodiment 1, the cold energy of natural gas is only used for condensing high temperature steam discharge；Embodiment 2 and embodiment 3
In, the cold energy of natural gas is only used for the cooling in condenser.But the cold energy of natural gas can also be used to make high temperature steam discharge simultaneously
Cooling in condensation and condenser, as shown in Figure 4.
In detail, the high temperature exhaust steam end of steam turbine 21 is connected to a port of triple valve 23；The second end of triple valve
Mouth is connected to condenser 22 via the first exhaust stream road 24.The flow path of first cooling medium can be using real in the condenser 22
The structure in example 2 is applied, it can also be using the structure for having installed Air-Cooling Island as embodiment 3 additional.
The third port of triple valve 23 is connected to the second exhaust stream road 25.Second exhaust stream road 25 is branched off into two steam discharge branches
25a,25b.Steam discharge branch 25a is connected to secondary heater 13, and the high temperature steam discharge flowed through in steam discharge branch 25a adds as second
The heat source of hot device 13.Steam discharge branch 25b is connected to primary heater 12, the high temperature steam discharge conduct flowed through in steam discharge branch 25b
The heat source of primary heater 12.
About the setting of heater, heater and the first cooling medium that high temperature steam discharge can be made to pass through or air-cooled air are passed through
The heater crossed shares；Also more heaters can be set, heater, the first cooling medium or the sky for passing through high temperature steam discharge
The heater that cold air passes through is heater set in addition each other.
Using the structure of the present embodiment, the condensation efficiency to high temperature steam discharge can be further increased, is further increased by vapour
The cycle efficieny of the Rankine cycle of the realizations such as turbine, condenser.
The present embodiment has following equilibrium relations:
QAlways=FLNG*QLNG gasification latent heat+FLNG*(TFor-T0)*CP gas=QThe steam discharge of first exhaust line+QThe steam discharge of second exhaust line=Q1+Q2+…+Qn。
Wherein, n indicates heater number, the heater number and the first cooling medium or air-cooled passed through including high temperature steam discharge
The heater number that air passes through；
QThe steam discharge of first exhaust line=QSeawater=QRecirculated water=QIt is air-cooled。
Embodiment 5
In embodiment 1 to embodiment 4,15a section quilt of the liquefied natural gas from LNG storage tank 11 through natural-gas transfer pipeline
Supply participates in the condensation of high temperature steam discharge to heater.But it is also possible to which cold energy is arranged in the 15a section of natural-gas transfer pipeline
The cold energy utilization devices such as stirling generator.
As shown in figure 5, the cold end 50a of cold energy stirling generator 50 is arranged in the 15a section of natural-gas transfer pipeline.It closes
In the structure and its working method of cold energy stirling generator and the invention main points of non-present invention, it is not described in detail herein.
The liquefied natural gas that -162 DEG C are exported from LNG storage tank 11 consumes cold energy through cold energy stirling generator 50, from cold energy
The temperature for the liquefied natural gas that stirling generator 50 is discharged is -35 DEG C.The liquefied natural gas that the initial temperature is -35 DEG C is supplied
To the heater in condenser system any in embodiment 1 to embodiment 4, the high temperature steam discharge of steam turbine is condensed.
In accordance with the present invention it is further possible to provide a kind of electricity generation system, which includes above-described embodiment 1 to embodiment 4
The steam and condensate system of middle any structure.
Above by embodiment and embodiment, the present invention is described, but those skilled in the art should know
Dawn can carry out various additional, changes, and these additional, change schemes should all in the case where not departing from present subject matter
It is understood to include within the scope of claims of the present invention.
Claims (12)
1. a kind of steam condensing method, the high temperature steam discharge for generating power generation turbine is condensed into condensed water, and feature exists
In, including following heat transfer process:
First heat transfer process, the high temperature steam discharge discharge thermal energy to the first cooling medium in First Heat Exchanger and form condensed water；
Second heat transfer process, the second cooling medium directly or indirectly carry out heat exchange with first cooling medium, and described the
One cooling medium absorbs the cold energy of second cooling medium, at the same time, described second in second heat transfer process
Cooling medium becomes gas phase natural gas from liquid natural gas by discharging the cold energy,
Before carrying out first heat transfer process, second heat transfer process, also, the thermal energy and the cold energy are carried out
Energy is roughly equal.
2. steam condensing method according to claim 1, which is characterized in that
Replace second heat transfer process, and be arranged with the parallel third heat transfer process of first heat transfer process,
In first heat transfer process, a part of the high temperature steam discharge is in the First Heat Exchanger and first cooling Jie
Matter carries out heat exchange and forms the first condensed water；
In the third heat transfer process, the rest part of the high temperature steam discharge is discharged in third heat exchanger to the second cooling medium
Thermal energy and form the second condensed water, at the same time, second cooling medium is by release cold energy from the liquid natural gas
Become the gas phase natural gas；
The thermal energy and second cooling Jie that the rest part of the high temperature steam discharge discharges in the third heat transfer process
The amount for the cold energy that matter discharges in the third heat transfer process is equal；
The process that the method also includes making first condensed water and second condensed water converge.
3. steam condensing method according to claim 1, which is characterized in that
The third heat transfer process parallel with first heat transfer process and the second heat transfer process is also set up,
In first heat transfer process, a part of the high temperature steam discharge is situated between in the First Heat Exchanger to first cooling
Matter discharges thermal energy and forms the first condensed water；
In the third heat transfer process, the rest part of the high temperature steam discharge is discharged in third heat exchanger to the second cooling medium
Thermal energy and form the second condensed water, at the same time, second cooling medium is become by release cold energy from liquid natural gas
Gas phase natural gas；
The institute of thermal energy and the high temperature steam discharge that described a part of the high-temperature gas discharges in first heat transfer process
The sum of the amount of thermal energy that rest part discharges in the third heat transfer process is stated, with second cooling medium described second
The sum of the amount of cold energy discharged in heat transfer process and the third heat transfer process is equal；
The process that the method also includes making first condensed water and second condensed water converge.
4. steam condensing method according to claim 1, which is characterized in that
When first cooling medium is recirculated water,
First cooling medium to have heated up in first heat transfer process through heat exchange is in second heat transfer process
In directly or indirectly carry out heat exchange with second cooling medium and cool down,
Desuperheated first cooling medium is back to the First Heat Exchanger in second heat transfer process, described
Heat exchange is carried out with the high temperature steam discharge in one heat transfer process.
It is special then be 5. steam condensing method according to claim 1,
When first cooling medium is the Lake Water, river or seawater that are not recycled,
Cool down in second heat transfer process through heat exchange from external first cooling medium, the desuperheated institute
It states the first cooling medium to be directed to the First Heat Exchanger and carry out heat exchange with the high temperature steam discharge, in first heat exchange
First cooling medium that device has heated up through heat exchange is discharged to the outside.
6. steam condensing method according to claim 1, which is characterized in that
In second heat transfer process, the cold energy is passed to air by second cooling medium, absorbs the cold energy
The air and first cooling medium carry out heat exchange, so that first cooling medium absorbs the cold energy.
7. a kind of steam and condensate system, the high temperature steam discharge for generating power generation turbine is condensed into condensed water and collects, feature
It is, comprising:
First Heat Exchanger makes the high temperature steam discharge form condensed water to the first cooling medium release thermal energy and collects；
Second heat exchanger makes first cooling medium and the second cooling medium directly carry out heat exchange, described first cooling Jie
Matter absorbs the cold energy of second cooling medium, and at the same time, second cooling medium is by discharging the cold energy from liquid
Phase natural gas becomes gas phase natural gas, also, the energy of the thermal energy and the cold energy is roughly equal；
High-temperature gas flow path is connect with the First Heat Exchanger, and the high temperature steam discharge is guided to the First Heat Exchanger；
First medium flow path makes the first cooling medium followed by second heat exchanger, the First Heat Exchanger；With
Second medium flow path makes second cooling medium flow through second heat exchanger.
8. steam and condensate system according to claim 7, which is characterized in that
The first medium flow path is circulation stream or non-circulation stream,
If the first medium flow path is circulation stream, first cooling medium followed by second heat exchanger and
Second heat exchanger is back to after the First Heat Exchanger；
If the first medium flow path is not circulation stream, from external first cooling medium followed by institute
It states after the second heat exchanger and the First Heat Exchanger and guides to outside.
9. steam and condensate system according to claim 7, which is characterized in that
Including multiple second heat exchangers, each second heat exchanger includes input terminal and the output of the second cooling medium
End enters second cooling medium of second heat exchanger after heat exchange discharges cold energy from described from the input terminal
Output end outflow,
At least two in multiple second heat exchangers connect in parallel or serial fashion,
The first medium flow path includes the first medium branch of multiple parallel connections, and each first medium branch is respectively by described
One cooling medium is guided to each second heat exchanger；
The amount for the cold energy that the amount of the thermal energy and second cooling medium discharge in each second heat exchanger it
With it is equal.
10. a kind of steam and condensate system, the high temperature steam discharge for generating power generation turbine is condensed into condensed water, which is characterized in that
Include:
First Heat Exchanger makes the high temperature steam discharge discharge thermal energy to the first cooling medium and form condensed water；
Second heat exchanger makes air and the second cooling medium carry out heat exchange, so that it is cooling so that the air is absorbed described second
The cold energy of medium, at the same time, second cooling medium become gas phase day from liquid natural gas by discharging the cold energy
Right gas, also, the energy of the thermal energy and the cold energy is roughly equal；
Air-cooling apparatus makes first cooling medium carry out heat exchange with the air for absorbing the cold energy, thus
First cooling medium is set to absorb the cold energy；
High-temperature gas flow path is connect with the First Heat Exchanger, and the high temperature steam discharge is guided to the First Heat Exchanger；
First medium flow path makes the first cooling medium followed by the air-cooling apparatus, the First Heat Exchanger；
Air flow circuit makes the air flow successively through second heat exchanger, the air-cooling apparatus；With
Second medium flow path makes second cooling medium flow through second heat exchanger.
11. a kind of steam and condensate system, the high temperature steam discharge for generating power generation turbine is condensed into condensed water and collects, feature
It is, comprising:
First Heat Exchanger makes a part of the high temperature steam discharge and the first cooling medium carry out heat exchange and form the first condensed water
And it collects；
Third heat exchanger makes the rest part of the high temperature steam discharge discharge thermal energy to the second cooling medium and form the second condensed water
And collect, at the same time, second cooling medium becomes gas phase natural gas from liquid natural gas by release cold energy, described
The thermal energy of the rest part release of high temperature steam discharge is equal with the amount of the cold energy that second cooling medium discharges；
First high temperature steam discharge flow path, is connected to the First Heat Exchanger, by a part guidance of the high temperature steam discharge to described the
One heat exchanger；
Second high temperature steam discharge flow path, is connected to the third heat exchanger, and the rest part of the high temperature steam discharge is guided to described
Third heat exchanger；
Wherein, second condensed water converges via pipeline with first condensed water.
12. a kind of electricity generation system, comprising: generator；It drives the generator to be generated electricity and the steam turbine of steam discharge is discharged；And
Steam and condensate system described in any one of claim 7 to 11.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910498798.XA CN110107368B (en) | 2019-06-11 | 2019-06-11 | Steam condensing method, steam condensing system and power generation system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910498798.XA CN110107368B (en) | 2019-06-11 | 2019-06-11 | Steam condensing method, steam condensing system and power generation system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN110107368A true CN110107368A (en) | 2019-08-09 |
| CN110107368B CN110107368B (en) | 2024-04-19 |
Family
ID=67494522
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910498798.XA Active CN110107368B (en) | 2019-06-11 | 2019-06-11 | Steam condensing method, steam condensing system and power generation system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN110107368B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113932213A (en) * | 2020-07-14 | 2022-01-14 | 国家能源投资集团有限责任公司 | Steam system of power generation steam turbine unit and coal-fired power generator unit |
Citations (22)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH05113108A (en) * | 1991-10-23 | 1993-05-07 | Osaka Gas Co Ltd | Cold heat power generator utilizing liquefied natural gas |
| WO2006104800A2 (en) * | 2005-03-30 | 2006-10-05 | Fluor Technologies Corporation | Configurations and methods for thermal integration of lng regasification and power plants |
| JP2007205187A (en) * | 2006-01-31 | 2007-08-16 | Hitachi Engineering & Services Co Ltd | Heat recovery system attached to boiler-steam turbine system |
| WO2008103067A1 (en) * | 2007-02-19 | 2008-08-28 | Vladimir Alekseevich Fedorov | Electrogenerating device with a high-temperature steam turbine |
| US20090025387A1 (en) * | 2005-11-04 | 2009-01-29 | Parsons Brinckerhoff Limited | Process and plant for power generation |
| JP2010276013A (en) * | 2010-02-03 | 2010-12-09 | Toshiaki Takashima | Power generation device |
| WO2013134553A1 (en) * | 2012-03-09 | 2013-09-12 | Bluelagoon Technologies Ltd | Apparatus and method for vapor driven absorption heat pumps and absorption heat transformer with applications |
| JP2014104847A (en) * | 2012-11-27 | 2014-06-09 | Mitsubishi Heavy Ind Ltd | Cold use device for low-temperature liquefied fuel |
| CN106150578A (en) * | 2015-04-20 | 2016-11-23 | 中国海洋石油总公司 | A kind of multistage coupling LNG cold energy use cycle generating system |
| CN107022768A (en) * | 2017-04-11 | 2017-08-08 | 赫普热力发展有限公司 | The system that a kind of utilization thermal power plant peak regulation electric power passes through alkaline electrolytic bath hydrogen manufacturing |
| CN107227981A (en) * | 2017-06-05 | 2017-10-03 | 华电电力科学研究院 | One kind utilizes LNG cold energy Collaborative Control turbine discharge back pressure system and method |
| CN107725130A (en) * | 2017-09-29 | 2018-02-23 | 江苏科技大学 | A kind of overcritical second diffluence formula longitudinal direction three-level Rankine cycle electricity generation system |
| US20180223696A1 (en) * | 2014-09-18 | 2018-08-09 | Mitsubishi Hitachi Power Systems, Ltd. | Cooling equipment, combined cycle plant comprising same, and cooling method |
| JP2018141452A (en) * | 2017-02-28 | 2018-09-13 | 三菱重工業株式会社 | Steam turbine system |
| CN108658154A (en) * | 2018-05-30 | 2018-10-16 | 江苏科技大学 | A kind of power generation of LNG cold energy heated type and seawater desalination system and its method of comprehensive utilization |
| CN109339973A (en) * | 2018-12-04 | 2019-02-15 | 上海理工大学 | A kind of cold energy of liquefied natural gas utilizes system |
| CN109630309A (en) * | 2018-11-12 | 2019-04-16 | 赫普科技发展（北京）有限公司 | LNG cold energy Stirling electricity generation system |
| KR20190052902A (en) * | 2017-11-09 | 2019-05-17 | 대우조선해양 주식회사 | Floating and storage power plant using cold heat of liquefied natural gas and generating method thereof |
| JP2019090352A (en) * | 2017-11-13 | 2019-06-13 | 一般財団法人電力中央研究所 | Industrial facility |
| CN209976590U (en) * | 2019-06-11 | 2020-01-21 | 赫普科技发展（北京）有限公司 | Steam condensing system and power generation system |
| CN111852601A (en) * | 2019-04-26 | 2020-10-30 | 赫普能源环境科技有限公司 | LNG cold energy CO2Working medium circulation power generation system and power generation method |
| CN212376702U (en) * | 2020-05-18 | 2021-01-19 | 东莞市粤湾新能源有限公司 | Steam turbine bypass system heated by combustion engine gas |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101121721B1 (en) * | 2010-01-28 | 2012-02-28 | 에스티엑스조선해양 주식회사 | Floating type LNG regasification unit |
| JP2013007324A (en) * | 2011-06-24 | 2013-01-10 | Mitsubishi Heavy Ind Ltd | Gas turbine, and gas turbine combined cycle power generation equipment |
| KR101434908B1 (en) * | 2013-05-23 | 2014-08-29 | 포스코에너지 주식회사 | System for producing hot heat source or electric power using waste heat, and method for controlling therof |
| CN103993922B (en) * | 2014-05-30 | 2016-03-30 | 西安交通大学 | A kind of low temperature exhaust heat CO 2rankine cycle system |
| CN106593553A (en) * | 2017-01-09 | 2017-04-26 | 大连理工大学 | Multi-level expansion power generation system recycling liquefied natural gas cold energy |
| JP6779146B2 (en) * | 2017-01-27 | 2020-11-04 | 株式会社神戸製鋼所 | Natural gas-fired combined cycle power generation system and natural gas-fired combined cycle power generation method |
-
2019
- 2019-06-11 CN CN201910498798.XA patent/CN110107368B/en active Active
Patent Citations (22)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH05113108A (en) * | 1991-10-23 | 1993-05-07 | Osaka Gas Co Ltd | Cold heat power generator utilizing liquefied natural gas |
| WO2006104800A2 (en) * | 2005-03-30 | 2006-10-05 | Fluor Technologies Corporation | Configurations and methods for thermal integration of lng regasification and power plants |
| US20090025387A1 (en) * | 2005-11-04 | 2009-01-29 | Parsons Brinckerhoff Limited | Process and plant for power generation |
| JP2007205187A (en) * | 2006-01-31 | 2007-08-16 | Hitachi Engineering & Services Co Ltd | Heat recovery system attached to boiler-steam turbine system |
| WO2008103067A1 (en) * | 2007-02-19 | 2008-08-28 | Vladimir Alekseevich Fedorov | Electrogenerating device with a high-temperature steam turbine |
| JP2010276013A (en) * | 2010-02-03 | 2010-12-09 | Toshiaki Takashima | Power generation device |
| WO2013134553A1 (en) * | 2012-03-09 | 2013-09-12 | Bluelagoon Technologies Ltd | Apparatus and method for vapor driven absorption heat pumps and absorption heat transformer with applications |
| JP2014104847A (en) * | 2012-11-27 | 2014-06-09 | Mitsubishi Heavy Ind Ltd | Cold use device for low-temperature liquefied fuel |
| US20180223696A1 (en) * | 2014-09-18 | 2018-08-09 | Mitsubishi Hitachi Power Systems, Ltd. | Cooling equipment, combined cycle plant comprising same, and cooling method |
| CN106150578A (en) * | 2015-04-20 | 2016-11-23 | 中国海洋石油总公司 | A kind of multistage coupling LNG cold energy use cycle generating system |
| JP2018141452A (en) * | 2017-02-28 | 2018-09-13 | 三菱重工業株式会社 | Steam turbine system |
| CN107022768A (en) * | 2017-04-11 | 2017-08-08 | 赫普热力发展有限公司 | The system that a kind of utilization thermal power plant peak regulation electric power passes through alkaline electrolytic bath hydrogen manufacturing |
| CN107227981A (en) * | 2017-06-05 | 2017-10-03 | 华电电力科学研究院 | One kind utilizes LNG cold energy Collaborative Control turbine discharge back pressure system and method |
| CN107725130A (en) * | 2017-09-29 | 2018-02-23 | 江苏科技大学 | A kind of overcritical second diffluence formula longitudinal direction three-level Rankine cycle electricity generation system |
| KR20190052902A (en) * | 2017-11-09 | 2019-05-17 | 대우조선해양 주식회사 | Floating and storage power plant using cold heat of liquefied natural gas and generating method thereof |
| JP2019090352A (en) * | 2017-11-13 | 2019-06-13 | 一般財団法人電力中央研究所 | Industrial facility |
| CN108658154A (en) * | 2018-05-30 | 2018-10-16 | 江苏科技大学 | A kind of power generation of LNG cold energy heated type and seawater desalination system and its method of comprehensive utilization |
| CN109630309A (en) * | 2018-11-12 | 2019-04-16 | 赫普科技发展（北京）有限公司 | LNG cold energy Stirling electricity generation system |
| CN109339973A (en) * | 2018-12-04 | 2019-02-15 | 上海理工大学 | A kind of cold energy of liquefied natural gas utilizes system |
| CN111852601A (en) * | 2019-04-26 | 2020-10-30 | 赫普能源环境科技有限公司 | LNG cold energy CO2Working medium circulation power generation system and power generation method |
| CN209976590U (en) * | 2019-06-11 | 2020-01-21 | 赫普科技发展（北京）有限公司 | Steam condensing system and power generation system |
| CN212376702U (en) * | 2020-05-18 | 2021-01-19 | 东莞市粤湾新能源有限公司 | Steam turbine bypass system heated by combustion engine gas |
Non-Patent Citations (2)
| Title |
|---|
| 刘国风;: "以二氧化碳作介质的冷凝汽轮机排汽的节能分析", 长春工程学院学报(自然科学版), no. 02, pages 60 * |
| 陈辉;陈修娟;肖立川;张栋栋;: "高性能动力***的技术进展与应用", 电力学报, no. 02, pages 19 - 22 * |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113932213A (en) * | 2020-07-14 | 2022-01-14 | 国家能源投资集团有限责任公司 | Steam system of power generation steam turbine unit and coal-fired power generator unit |
| CN113932213B (en) * | 2020-07-14 | 2024-04-05 | 国家能源投资集团有限责任公司 | Steam-water system of power generation turbine unit and coal-fired power generation unit |
Also Published As
| Publication number | Publication date |
|---|---|
| CN110107368B (en) | 2024-04-19 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN100462531C (en) | System and method for improving efficiency of combined cycle electric power plant | |
| CN102449271B (en) | Steam power cycle device | |
| CN103547786B (en) | Compound electricity generation system | |
| CN105003351A (en) | Multi-energy-form output energy tower for stepwise recycling gas engine waste heat energy | |
| CN104963776A (en) | Solar heat-complementary combined cycle power generation system | |
| US20140290244A1 (en) | Binary power generation system | |
| CN104912669A (en) | Fed air conditioning system of gas-steam combined cycle power plant and use method of fed air conditioning system | |
| AU2010269395A1 (en) | Vapor supply device | |
| JP2013180625A (en) | Exhaust heat recovery type ship propulsion device, and operation method therefor | |
| CN102155299A (en) | Combination system of stirling engine and combustion gas turbine utilizing liquefied natural gas | |
| CN101705849B (en) | Self-coupling cold source heat pump circulating device of low-temperature exhaust heat power generating system in low temperature exhaust steam condensation process | |
| US10344626B2 (en) | Hybrid power generation system | |
| CN103821571A (en) | Novel thermal power generation system and working method | |
| CN110107368A (en) | Steam condensing method, steam and condensate system and electricity generation system | |
| CN105508055B (en) | The system and method for distributed busbar protection cooling circulating water | |
| CN209976590U (en) | Steam condensing system and power generation system | |
| US20130318972A1 (en) | Gas turbine apparatus with improved exergy recovery | |
| CN215633192U (en) | LNG cold energy utilization device | |
| CN103775140A (en) | Improved electricity generation system with pump assisting in condensing and cooling and electricity generation method of electricity generation system | |
| CN107289665B (en) | Regional energy supply system | |
| KR101935637B1 (en) | Combined cycle power generation system | |
| CN114412595A (en) | Fuel smoke multi-temperature-zone utilization power generation system | |
| CN113309591A (en) | LNG cold energy utilization device | |
| CN204716400U (en) | The air inlet air conditioning system of Combined cycle gas-steam turbine power plant | |
| JP7121185B2 (en) | Power plant including natural gas regasification |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |