WO2012157285A1 - Système de génération d'énergie composite - Google Patents

Système de génération d'énergie composite Download PDF

Info

Publication number
WO2012157285A1
WO2012157285A1 PCT/JP2012/003266 JP2012003266W WO2012157285A1 WO 2012157285 A1 WO2012157285 A1 WO 2012157285A1 JP 2012003266 W JP2012003266 W JP 2012003266W WO 2012157285 A1 WO2012157285 A1 WO 2012157285A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
gas
power generation
turbine
gas engine
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.)
Ceased
Application number
PCT/JP2012/003266
Other languages
English (en)
Japanese (ja)
Inventor
芳一 広地
松本　忠士
寿英 平井
豊充 金井
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Chiyoda Corp
Original Assignee
Chiyoda Corp
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Chiyoda Corp filed Critical Chiyoda Corp
Priority to SG2013082441A priority Critical patent/SG194827A1/en
Priority to CN201280023975.5A priority patent/CN103547786B/zh
Priority to KR1020137030263A priority patent/KR101619393B1/ko
Publication of WO2012157285A1 publication Critical patent/WO2012157285A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Images

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
    • F01K23/06—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 combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—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 combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of 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
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/08—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for using special vapours
    • 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
    • Y02E20/14—Combined heat and power generation [CHP]
    • 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]

Definitions

  • the present invention relates to a combined power generation system, and more particularly to a gas engine combined power generation system that generates power using exhaust heat of a gas engine.
  • a combined power generation system in which power generation efficiency is improved by generating power using exhaust heat of internal combustion power generation has been widespread.
  • a Rankine cycle heating source including a gas turbine driven by combustion gas and a steam turbine driven by steam generated by collecting exhaust heat of the gas turbine, and using steam on the steam turbine side as a working fluid
  • Patent Document 1 A combined power generation system that improves power generation efficiency by using gas turbine exhaust gas is known (see Patent Document 1).
  • exhaust heat at two different temperature levels (for example, exhaust gas from 400 to 500 ° C and exhaust heat from engine jacket cooling water at 85 ° C) accounts for a large proportion of the total exhaust heat. Therefore, it is indispensable to use them effectively in order to improve power generation efficiency and reduce carbon dioxide emissions.
  • Patent Document 1 when the conventional technique described in Patent Document 1 is applied to the gas engine combined power generation system, there is a problem that the relatively low temperature engine jacket cooling water heat cannot be effectively used.
  • a cooling source below freezing point for example, LNG (Liquefied Natural Gas) cooling, refrigerator brine cooling, etc.
  • LNG Liquefied Natural Gas
  • refrigerator brine cooling etc.
  • the present invention has been devised in view of such problems of the prior art, and provides a combined power generation system capable of improving power generation efficiency by effectively using exhaust heat of a gas engine.
  • the main purpose is to do.
  • a gas engine (2) using combustible gas as fuel, a first generator (4) driven by the gas engine, and a hydrocarbon system A refrigerant turbine (3) using the refrigerant as a working fluid, a second generator (5) driven by the refrigerant turbine, and a first heater that heats the refrigerant using a coolant that cools the gas engine as a heat source (31), a second heater (11) for further heating the refrigerant heated by the first heater using the exhaust gas of the gas engine as a heat source, and condensation for condensing the refrigerant discharged from the refrigerant turbine And a vessel (22).
  • the refrigerant turbine that uses a hydrocarbon-based refrigerant as the working fluid is configured to use the exhaust heat of the gas engine (heat of exhaust gas and coolant), the exhaust heat recovery rate of the gas engine increases, The power generation efficiency of the system can be improved.
  • a gas engine (2) using combustible gas as a fuel, a first generator (4) driven by the gas engine, and a hydrocarbon-based refrigerant as a working fluid.
  • the refrigerant turbine that uses a hydrocarbon-based refrigerant as the working fluid is configured to use the exhaust heat of the gas engine (heat of exhaust gas and coolant), the exhaust heat recovery rate of the gas engine increases, The power generation efficiency of the system can be improved.
  • the refrigerant is heated by using the coolant heated by the exhaust gas of the gas engine without directly exchanging heat between the combustible hydrocarbon refrigerant and the exhaust gas of the gas engine, the safety of the system is increased. There are also advantages.
  • the condenser condenses the refrigerant using liquefied natural gas.
  • the combustible gas is a boil-off gas of liquefied natural gas.
  • boil-off gas generated from an LNG base or the like can be used effectively without requiring adjustment of heat quantity by mixing LP gas or the like as in the case of using as city gas.
  • the condenser condenses the refrigerant using brine.
  • the refrigerant is a mixed medium of methane and propane.
  • FIG. 1 is a configuration diagram showing an outline of a gas engine combined power generation system 1 according to a first embodiment of the present invention.
  • the combined power generation system 1 includes a gas engine 2 that is an internal combustion engine using a combustible gas as a fuel, and a refrigerant turbine 3 that uses a hydrocarbon-based refrigerant boiling at a low temperature (a temperature lower than water) as a working fluid.
  • the first generator 4 and the second generator 5 that are driven by the engine 2 and the refrigerant turbine 3, respectively, generate power, and are juxtaposed to the LNG base 6 that delivers LNG for city gas.
  • Boil-off gas (hereinafter referred to as BOG) generated at the LNG base 6 is supplied to the gas engine 2 as fuel (at least a part thereof), and the gas engine exhaust gas at a relatively high temperature (here 410 ° C.) after combustion is supplied. It is discharged toward the heat exchanger 11 for exhaust heat recovery.
  • the gas engine 2 is provided with a cooling engine jacket (not shown), and jacket cooling water at a relatively low temperature (88 ° C. in this case) is discharged from the engine jacket.
  • the discharged jacket cooling water is circulated through the cooling water circulation line 13 provided with the cooling water pump 12 in the direction indicated by the arrow in FIG.
  • the output of the gas engine 2 is converted into electric power by the first generator 4.
  • a mixed refrigerant of methane and propane (here, methane 50 to 55% by weight, propane 45 to 50% by weight) is used as a working fluid.
  • This working fluid is heated by the gas engine exhaust gas in the heat exchanger 11 before being introduced into the refrigerant turbine 3.
  • the heat exchanger 11 is provided with a plurality of heating units composed of heat transfer tube groups, so that efficient heat exchange between the gas engine exhaust gas and the working fluid is possible.
  • a working fluid (gas) having a predetermined temperature and pressure (here, 103 ° C., 4.9 MPaG) is introduced into the refrigerant turbine 3, and turbine blades (not shown) are rotated by the kinetic energy of the working fluid.
  • the output is converted into electric power by the second generator 5.
  • the working fluid discharged from the refrigerant turbine 3 (here, gas of temperature: ⁇ 5 ° C., pressure: 0.4 MPaG) is sent to the condenser 22 through the refrigerant circulation line 21 in the direction indicated by the arrow in FIG.
  • a discharge pipe 23 from the LNG base 6 is connected to the condenser 22, and the cold heat of the introduced LNG (here, temperature: ⁇ 160 ° C., pressure: 7.0 MPaG, flow rate: 70 t / hr) is the working fluid. Used for cooling. On the other hand, the heat of the working fluid is used to vaporize LNG.
  • the condensed working fluid is temporarily stored in a circulating refrigerant storage tank 25 provided in the refrigerant circulation line 21. Thereafter, the working fluid (here, ⁇ 128 ° C., 5.0 MPaG, 99.4 t / hr) pressurized by the refrigerant pump 26 provided in the refrigerant circulation line 21 is sent to the refrigerant evaporator 27.
  • the refrigerant evaporator 27 is connected to a seawater introduction pipe 28 for introducing seawater (here, 15 ° C.), and the working fluid is heated to a temperature at which the jacket cooling water does not freeze due to heat exchange with the seawater (here, 5 °C).
  • the working fluid from the refrigerant evaporator 27 is sent to the refrigerant heater 31 where it is heated by heat exchange with jacket cooling water (88 ° C., 270 t / hr here) (here, heated to 29 ° C.). ) On the other hand, the jacket cooling water is cooled to a temperature at which the gas engine 2 can be cooled in the refrigerant heater 31 (here, 50 to 80 ° C.). The working fluid from the refrigerant heater 31 is sent to the heat exchanger 11, and the heated working fluid (103 ° C., 4.9 MPaG) is supplied to the refrigerant turbine 3 again.
  • jacket cooling water 88 ° C., 270 t / hr here
  • the jacket cooling water is cooled to a temperature at which the gas engine 2 can be cooled in the refrigerant heater 31 (here, 50 to 80 ° C.).
  • the working fluid from the refrigerant heater 31 is sent to the heat exchanger 11, and the heated working fluid (
  • LNG from the LNG base 6 is discharged from the condenser 22 and then sent to the LNG heater 32 through the discharge pipe 23.
  • the LNG heater 32 is connected to a seawater introduction pipe 33 for introducing seawater (here, 15 ° C.), and the working fluid is heated by heat exchange with seawater (here, a gas at 5 ° C. Sent to the city gas line for use as city gas.
  • the BOG supply amount is 1.94 t / hr (fuel consumption is 29600 kw), and the exhaust amount of the gas engine exhaust gas is 83.2 t / hr.
  • the amount of power generated by the first generator 4 is 13500 kW, and the amount of power generated by the refrigerant turbine 3 is 4060 KW.
  • the total power generation efficiency of the combined power generation system 1 is 59.3% (the effective power generation efficiency including auxiliary power consumption is 57.2%), and a higher power generation efficiency can be realized as compared with a combined power generation system using a conventional gas turbine.
  • a conventional combined power generation system 201 using a gas turbine is shown in FIG.
  • BOG supply amount: 2.02 t / hr, consumed fuel: 30706 kW, pressure: 0.02 MPaG
  • the discharged gas turbine exhaust gas (temperature: 504 ° C., flow rate: 136.2 t / hr) is introduced into the exhaust gas boiler 204 for exhaust heat recovery.
  • the exhaust gas boiler 204 heat exchange is performed between the gas turbine exhaust gas and the steam, and the high-pressure steam (temperature: 482 ° C, pressure: 5.4MPaG, flow rate: 14.6t / hr) generated thereby is sent to the steam turbine generator 205. be introduced.
  • Exhaust steam (temperature: 41 ° C., pressure: 0.093 MPaG) from the steam turbine generator 205 is cooled in the condenser 206, and again through the condenser pump 207, the deaerator 208, and the high-pressure feed water pump 209, the exhaust gas boiler. Cycled to 204.
  • the cooling water introduced into the condenser 206 is circulated through the air cooling cooling tower 210.
  • the amount of power generated by the gas turbine generator is 9754kW, and the amount of power generated by the steam turbine generator is 3656kW.
  • the total power generation efficiency of the combined power generation system 201 is 47.3% (the effective power generation efficiency including auxiliary power consumption is 41.1%).
  • the gas turbine exhaust gas and the jacket cooling water are used as a high heat source by the refrigerant turbine 3 using a mixed refrigerant of methane and propane as a working fluid. Electricity is generated by the binary Rankine cycle method using the cold heat during gasification as a low heat source.
  • the exhaust heat recovery rate can be increased by effectively using the heat of the gas engine exhaust gas and the jacket cooling water, which occupy a large proportion of the exhaust heat of the gas engine 2, and thus the power generation efficiency of the combined power generation system 1 is improved.
  • the heating temperature in the heat exchanger 11 is preferably relatively low (for example, 130 ° C. or less) from the viewpoint of system safety.
  • the working fluid is condensed using LNG in the condenser 22, it is possible to effectively use the cold heat of the LNG discharged from the LNG base 6 or the like in the cooling process of the refrigerant.
  • BOG is used as the fuel gas (or part thereof) of the gas engine 2, it is generated from the LNG base 6 and the like without the need for adjusting the amount of heat by mixing LP gas or the like as in the case of use as city gas. BOG can be effectively used, and the cold heat of LNG can be effectively utilized in the cooling process of the working fluid.
  • FIG. 2 is a configuration diagram showing an outline of the gas engine combined power generation system 1 according to the second embodiment of the present invention.
  • the same components as those in the first embodiment described above are denoted by the same reference numerals. Further, in the second embodiment, the detailed description is omitted as in the case of the first embodiment except for the matters specifically mentioned below.
  • the second embodiment is different from the first embodiment in that the gas engine exhaust gas and the working fluid are indirectly heat-exchanged via jacket cooling water.
  • the jacket cooling water discharged from the gas engine 2 is sent to the heat exchanger 11A and heated by heat exchange with the gas engine exhaust gas. Thereafter, the jacket cooling water (here, pressurized hot water of 150 to 160 ° C.) is sent to the refrigerant heater 31A through the cooling water circulation line 13 and used for heating the working fluid.
  • the jacket cooling water cooled by the refrigerant heater 31A is supplied again to the engine jacket by the cooling water pump 12.
  • the working fluid (103 ° C., 4.9 MPaG) heated by the refrigerant heater 31 ⁇ / b> A is supplied to the refrigerant turbine 3.
  • the combined power generation system 1 according to the second embodiment has an advantage that the safety of the system is increased because the gas engine exhaust gas and the combustible working fluid are not directly heat-exchanged.
  • FIG. 3 is a configuration diagram showing an outline of the combined power generation system 100 according to the third embodiment of the present invention. 3, the same code
  • the combined power generation system 100 mainly includes a refrigerant turbine 3 using a hydrocarbon-based refrigerant boiling at a low temperature as a working fluid, and a generator 4 driven by the refrigerant turbine 3, and serves as a discharge source of steam and hot water. It is installed in parallel with a factory that does not (for example, petrochemical factory).
  • propane alone or a refrigerant obtained by mixing propane with a small amount of ethane or butane is used as a working fluid.
  • the working fluid is heated by exchanging heat with warm water (here, 100 ° C., 24.3 Gcal / hr) in the refrigerant heater 131 before being introduced into the refrigerant turbine 3.
  • warm water here, 100 ° C., 24.3 Gcal / hr
  • hot water (hot water) discharged from a factory or low-pressure steam can be used.
  • a working fluid having a predetermined temperature and pressure (here, 90 ° C., 3 MPaG) is introduced into the refrigerant turbine 3, and turbine blades (not shown) are rotated by the kinetic energy of the working fluid, and the output thereof is a generator. 4 is converted into electric power.
  • the working fluid discharged from the refrigerant turbine 3 (here, 20 ° C., 0.5 MPaG gas) is sent to the condenser 122 through the refrigerant circulation line 121 in the direction indicated by the arrow in FIG.
  • a brine circulation line 42 from the vapor absorption refrigerator 41 is connected to the condenser 122, and the cold of the introduced brine (here, ⁇ 8 ° C., 21.4 Gcal / hr ethylene glycol) is used as the working fluid. Used for cooling.
  • low-pressure steam for example, saturated steam of 0.5 to 0.7 MPaG discharged from the factory is used as a heat source.
  • the working fluid (2 ° C.) cooled in the condenser 122 is temporarily stored in the circulating refrigerant storage tank 25 on the refrigerant circulation line 21. Thereafter, the working fluid whose pressure has been increased by the refrigerant pump 26 is sent to the refrigerant heater 131, where the working fluid (90 ° C., 3 MPaG) heated again is supplied to the refrigerant turbine 3.
  • hot water discharged from the factory is used as a high heat source, and brine cold using the low-pressure steam discharged from the factory is used as a low heat source to generate power.
  • no new fuel such as LNG
  • chiller water of a factory can be used instead of brine.
  • the combined power generation system 100 is configured to condense the refrigerant discharged from the refrigerant turbine using brine, a highly efficient power generation amount can be realized.
  • the condenser 122 is supplied with cooling water (25 ° C., 22.6 Gcal / hr) (conventional technology).
  • the working fluid discharged from the refrigerant turbine 3 has a temperature of 50 ° C. and a pressure of 1.2 MPaG, and is cooled by the cooling water in the condenser 122.
  • the cooled working fluid (35 ° C.) is temporarily stored in the circulating refrigerant storage tank 125 on the refrigerant circulation line 21. And the electric power generation amount by the generator 4 becomes a low value (2500 kW) compared with the case where it condenses using the brine cold heat of this invention (4000 kW).
  • the present invention has been described based on specific embodiments, these embodiments are merely examples, and the present invention is not limited to these embodiments.
  • the working fluid of the refrigerant turbine is not limited to the above-described one, but a hydrocarbon-based refrigerant composed of a simple substance such as methane, ethane, propane, or butane having a relatively small molecular weight or a mixture of two or more thereof. Can be used.
  • the weight ratio of the hydrocarbon components can be set according to the temperature levels of the high heat source and the low heat source in the applied combined power generation system. It should be noted that all the components of the combined power generation system according to the present invention shown in the above embodiment are not necessarily essential, and can be appropriately selected as long as they do not depart from the scope of the present invention.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Abstract

L'invention concerne un système de génération d'énergie composite dont l'efficacité de génération d'énergie est améliorée grâce à l'utilisation efficace de la chaleur du gaz d'échappement d'un moteur à gaz. Un système de génération d'énergie composite comprend : un moteur à gaz (2) dans lequel un BOG est utilisé comme combustible ; un premier générateur d'énergie (4) entraîné par le moteur à gaz ; une turbine de réfrigérant (3) dans laquelle un réfrigérant mélangé à base d'hydrocarbure est utilisé comme fluide de travail ; un second générateur d'énergie (5) entraîné par la turbine de réfrigérant ; un dispositif de chauffage de réfrigérant (31) permettant de chauffer le réfrigérant mélangé au moyen d'un liquide de refroidissement permettant de refroidir le moteur à gaz comme source de chaleur ; un échangeur de chaleur (11) permettant de chauffer davantage le réfrigérant mélangé chauffé par le dispositif de chauffage de réfrigérant au moyen du gaz d'échappement du moteur à gaz comme source de chaleur ; et un condensateur (22) permettant de condenser le réfrigérant mélangé évacué depuis ladite turbine de réfrigérant.
PCT/JP2012/003266 2011-05-19 2012-05-18 Système de génération d'énergie composite Ceased WO2012157285A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
SG2013082441A SG194827A1 (en) 2011-05-19 2012-05-18 Composite power generation system
CN201280023975.5A CN103547786B (zh) 2011-05-19 2012-05-18 复合发电系统
KR1020137030263A KR101619393B1 (ko) 2011-05-19 2012-05-18 복합 발전 시스템

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011112013A JP5875253B2 (ja) 2011-05-19 2011-05-19 複合発電システム
JP2011-112013 2011-05-19

Publications (1)

Publication Number Publication Date
WO2012157285A1 true WO2012157285A1 (fr) 2012-11-22

Family

ID=47176631

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2012/003266 Ceased WO2012157285A1 (fr) 2011-05-19 2012-05-18 Système de génération d'énergie composite

Country Status (6)

Country Link
JP (1) JP5875253B2 (fr)
KR (1) KR101619393B1 (fr)
CN (1) CN103547786B (fr)
MY (1) MY173872A (fr)
SG (1) SG194827A1 (fr)
WO (1) WO2012157285A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180340452A1 (en) * 2015-11-13 2018-11-29 Shell Oil Company Method of generating power using a combined cycle
CN109233926A (zh) * 2018-07-24 2019-01-18 北京宏科庆能科技有限公司 Bog发电机烟气的吸收式预冷系统

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9366238B2 (en) * 2013-03-13 2016-06-14 Lockheed Martin Corporation System and process of cooling an OTEC working fluid pump motor
JP6284734B2 (ja) * 2013-10-09 2018-02-28 日野自動車株式会社 ランキンサイクルシステム
KR101610520B1 (ko) * 2014-10-10 2016-04-08 현대자동차주식회사 이원화된 유체순환회로를 갖는 차량용 랭킨사이클 시스템 및 제어방법
CN105698002B (zh) * 2016-01-14 2018-11-06 新奥科技发展有限公司 移动能源站及其能量利用方法
CN105715952B (zh) * 2016-02-19 2018-10-12 新奥科技发展有限公司 移动能源站及其能量利用方法
IT201600121407A1 (it) * 2016-11-30 2018-05-30 Saipem Spa Ciclo a gas chiuso in applicazioni criogeniche o fluidi refrigeranti
CN108019275B (zh) * 2016-12-21 2020-12-29 赵志渊 一种基于复杂工况的燃气内燃机发电功率及排烟参数的计算方法
US10627158B2 (en) * 2017-03-13 2020-04-21 Baker Hughes, A Ge Company, Llc Coproduction of liquefied natural gas and electric power with refrigeration recovery
JP6928937B2 (ja) 2019-05-21 2021-09-01 日揮グローバル株式会社 発電システム及び発電方法
WO2021229637A1 (fr) * 2020-05-11 2021-11-18 日揮グローバル株式会社 Système et procédé de réglage de température
JP7725386B2 (ja) * 2022-02-09 2025-08-19 三菱重工業株式会社 冷熱回収設備及び船舶
JP7760480B2 (ja) * 2022-10-13 2025-10-27 三菱重工業株式会社 冷熱発電装置、及び冷熱発電システム

Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05113108A (ja) * 1991-10-23 1993-05-07 Osaka Gas Co Ltd 液化天然ガスを用いる冷熱発電装置
JP2000345915A (ja) * 1999-06-07 2000-12-12 Nissan Motor Co Ltd 動力装置
JP2002129980A (ja) * 2000-10-25 2002-05-09 Osaka Gas Co Ltd コンバインドサイクル発電装置
JP2006037760A (ja) * 2004-07-23 2006-02-09 Sanden Corp ランキンサイクル発電装置
JP2006144744A (ja) * 2004-11-24 2006-06-08 Toyota Industries Corp 車両用排熱回収システム
JP2007255363A (ja) * 2006-03-24 2007-10-04 Osaka Gas Co Ltd 動力システム
WO2008047489A1 (fr) * 2007-04-11 2008-04-24 Hitachi, Ltd. Équipement d'alimentation pour une installation de liquéfaction de gaz naturel
JP2008128254A (ja) * 2006-11-24 2008-06-05 Behr Gmbh & Co Kg 少なくとも１つの膨張装置を駆動するための有機ランキンサイクル循環を備えたシステム及び膨張装置を駆動するための熱交換器並びに少なくとも１つの膨張装置を運転するための方法
JP2008231980A (ja) * 2007-03-19 2008-10-02 Sanden Corp 内燃機関の廃熱利用装置
JP2010156314A (ja) * 2009-01-05 2010-07-15 Toyota Motor Corp 廃熱回収装置、及びエンジン
JP2010203284A (ja) * 2009-03-02 2010-09-16 Nissan Motor Co Ltd 排熱回生システム
JP2011012625A (ja) * 2009-07-03 2011-01-20 Mitsubishi Electric Corp 排熱回生システムおよびその制御方法
JP2011027000A (ja) * 2009-07-23 2011-02-10 Sanden Corp 廃熱利用装置
JP2011085071A (ja) * 2009-10-15 2011-04-28 Toyota Industries Corp 廃熱回生システム

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3888084A (en) * 1974-05-20 1975-06-10 Gilbert L Hawkins Thermal recovery system
JPS5620709A (en) * 1979-07-27 1981-02-26 Hitachi Ltd Method of recovering cold and hot energy
JP2002161716A (ja) * 2000-11-29 2002-06-07 Yanmar Diesel Engine Co Ltd 廃熱回収ランキンサイクルシステム及び廃熱回収方法
US6857268B2 (en) * 2002-07-22 2005-02-22 Wow Energy, Inc. Cascading closed loop cycle (CCLC)
EG24658A (en) * 2002-09-30 2010-04-07 Bpcorporation North America In All electric lng system and process
JP4404010B2 (ja) * 2005-05-26 2010-01-27 Ｊｆｅエンジニアリング株式会社 複合冷熱発電装置
GB2457266B (en) * 2008-02-07 2012-12-26 Univ City Generating power from medium temperature heat sources
CN101614139A (zh) * 2009-07-31 2009-12-30 王世英 多循环发电热力系统

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05113108A (ja) * 1991-10-23 1993-05-07 Osaka Gas Co Ltd 液化天然ガスを用いる冷熱発電装置
JP2000345915A (ja) * 1999-06-07 2000-12-12 Nissan Motor Co Ltd 動力装置
JP2002129980A (ja) * 2000-10-25 2002-05-09 Osaka Gas Co Ltd コンバインドサイクル発電装置
JP2006037760A (ja) * 2004-07-23 2006-02-09 Sanden Corp ランキンサイクル発電装置
JP2006144744A (ja) * 2004-11-24 2006-06-08 Toyota Industries Corp 車両用排熱回収システム
JP2007255363A (ja) * 2006-03-24 2007-10-04 Osaka Gas Co Ltd 動力システム
JP2008128254A (ja) * 2006-11-24 2008-06-05 Behr Gmbh & Co Kg 少なくとも１つの膨張装置を駆動するための有機ランキンサイクル循環を備えたシステム及び膨張装置を駆動するための熱交換器並びに少なくとも１つの膨張装置を運転するための方法
JP2008231980A (ja) * 2007-03-19 2008-10-02 Sanden Corp 内燃機関の廃熱利用装置
WO2008047489A1 (fr) * 2007-04-11 2008-04-24 Hitachi, Ltd. Équipement d'alimentation pour une installation de liquéfaction de gaz naturel
JP2010156314A (ja) * 2009-01-05 2010-07-15 Toyota Motor Corp 廃熱回収装置、及びエンジン
JP2010203284A (ja) * 2009-03-02 2010-09-16 Nissan Motor Co Ltd 排熱回生システム
JP2011012625A (ja) * 2009-07-03 2011-01-20 Mitsubishi Electric Corp 排熱回生システムおよびその制御方法
JP2011027000A (ja) * 2009-07-23 2011-02-10 Sanden Corp 廃熱利用装置
JP2011085071A (ja) * 2009-10-15 2011-04-28 Toyota Industries Corp 廃熱回生システム

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180340452A1 (en) * 2015-11-13 2018-11-29 Shell Oil Company Method of generating power using a combined cycle
RU2720873C2 (ru) * 2015-11-13 2020-05-13 Шелл Интернэшнл Рисерч Маатсхаппий Б.В. Способ генерирования энергии с помощью комбинированного цикла
AU2019268076B2 (en) * 2015-11-13 2021-03-11 Shell Internationale Research Maatschappij B.V. Method of generating power using a combined cycle
CN109233926A (zh) * 2018-07-24 2019-01-18 北京宏科庆能科技有限公司 Bog发电机烟气的吸收式预冷系统

Also Published As

Publication number Publication date
CN103547786B (zh) 2016-05-18
SG194827A1 (en) 2013-12-30
JP2012241604A (ja) 2012-12-10
JP5875253B2 (ja) 2016-03-02
CN103547786A (zh) 2014-01-29
KR101619393B1 (ko) 2016-05-10
KR20140027269A (ko) 2014-03-06
MY173872A (en) 2020-02-25

Similar Documents

Publication Publication Date Title
JP5875253B2 (ja) 複合発電システム
Liu et al. A review of research on the closed thermodynamic cycles of ocean thermal energy conversion
CN109386316B (zh) 一种lng冷能和bog燃烧能联合利用系统及方法
US12221922B2 (en) Organic rankine cycle (ORC) power generation system utilizing LNG cold energy and dual-fuel marine engine waste heat
US8661820B2 (en) LNG regasification and power generation
KR20210089635A (ko) 복합 사이클 발전소용 유기 랭킨 사이클
CN104214507A (zh) 液化气处理系统
US11300010B2 (en) Cooling equipment, combined cycle plant comprising same, and cooling method
JP2013011272A (ja) 発電システム
KR20130091806A (ko) 히트펌프를 사용하는 열병합 발전시스템
CN107178927B (zh) 一种lng动力船的bog利用系统及工作方法
JP7698146B2 (ja) 混合作動流体を利用したｌｎｇ冷熱発電
JPH10288047A (ja) 液化天然ガス気化発電装置
CN103821571A (zh) 一种新型火力发电系统及工作方法
KR101528935B1 (ko) 복수기 폐열 발전시스템
CN217841760U (zh) 利用lng冷能联合循环发电、供冷及余热回收系统
KR20130099616A (ko) 액화천연가스 연료의 기화를 이용한 액화천연가스 연료 추진 선박용 유기 랭킨 사이클 발전 시스템 및 방법
KR20130099617A (ko) 액화천연가스 화물창의 냉열을 이용한 액화천연가스 운반선용 유기 랭킨 사이클 발전 시스템 및 방법
KR101419009B1 (ko) 복합화력발전설비를 구비한 엘엔지 재기화 설비
CN111852598A (zh) 船舶余热回收发电系统
JP2010096414A (ja) アンモニア吸収冷凍式発電装置
KR101616333B1 (ko) 액화천연가스 재기화장치
CN116838940A (zh) 一种利用余热锅炉烟气废热的lng气化系统
JP2005147447A (ja) アンモニア−水非共沸混合媒体循環システム
CA2983533C (fr) Generation d'energie a cycles combines

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 12785115

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 20137030263

Country of ref document: KR

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 12785115

Country of ref document: EP

Kind code of ref document: A1