WO2016195230A1 - 선박 - Google Patents

선박 Download PDF

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Publication number
WO2016195230A1
WO2016195230A1 PCT/KR2016/003542 KR2016003542W WO2016195230A1 WO 2016195230 A1 WO2016195230 A1 WO 2016195230A1 KR 2016003542 W KR2016003542 W KR 2016003542W WO 2016195230 A1 WO2016195230 A1 WO 2016195230A1
Authority
WO
WIPO (PCT)
Prior art keywords
gas
boil
valve
compressor
heat exchanger
Prior art date
Application number
PCT/KR2016/003542
Other languages
English (en)
French (fr)
Korean (ko)
Inventor
신현준
최동규
문영식
안수경
장현민
손재욱
이준채
Original Assignee
대우조선해양 주식회사
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
Priority claimed from KR1020150136257A external-priority patent/KR20160098953A/ko
Application filed by 대우조선해양 주식회사 filed Critical 대우조선해양 주식회사
Priority to PL16803585.5T priority Critical patent/PL3305645T3/pl
Priority to CN201680045491.9A priority patent/CN107922035B/zh
Priority to SG11201710005RA priority patent/SG11201710005RA/en
Priority to JP2017562355A priority patent/JP6899335B2/ja
Priority to RU2017145881A priority patent/RU2703370C2/ru
Priority to US15/579,582 priority patent/US10399655B2/en
Priority to EP16803585.5A priority patent/EP3305645B1/en
Publication of WO2016195230A1 publication Critical patent/WO2016195230A1/ko
Priority to PH12017502174A priority patent/PH12017502174A1/en

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63H—MARINE PROPULSION OR STEERING
    • B63H21/00—Use of propulsion power plant or units on vessels
    • B63H21/38—Apparatus or methods specially adapted for use on marine vessels, for handling power plant or unit liquids, e.g. lubricants, coolants, fuels or the like
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63B—SHIPS OR OTHER WATERBORNE VESSELS; EQUIPMENT FOR SHIPPING 
    • B63B25/00—Load-accommodating arrangements, e.g. stowing, trimming; Vessels characterised thereby
    • B63B25/02—Load-accommodating arrangements, e.g. stowing, trimming; Vessels characterised thereby for bulk goods
    • B63B25/08—Load-accommodating arrangements, e.g. stowing, trimming; Vessels characterised thereby for bulk goods fluid
    • B63B25/12—Load-accommodating arrangements, e.g. stowing, trimming; Vessels characterised thereby for bulk goods fluid closed
    • B63B25/16—Load-accommodating arrangements, e.g. stowing, trimming; Vessels characterised thereby for bulk goods fluid closed heat-insulated
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F02M21/0218—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers
    • F02M21/0287—Details on the gaseous fuel supply system, e.g. tanks, valves, pipes, pumps, rails, injectors or mixers characterised by the transition from liquid to gaseous phase ; Injection in liquid phase; Cooling and low temperature storage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C6/00—Methods and apparatus for filling vessels not under pressure with liquefied or solidified gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C9/00—Methods or apparatus for discharging liquefied or solidified gases from vessels not under pressure
    • F17C9/02—Methods or apparatus for discharging liquefied or solidified gases from vessels not under pressure with change of state, e.g. vaporisation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/0002—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the fluid to be liquefied
    • F25J1/0022—Hydrocarbons, e.g. natural gas
    • F25J1/0025—Boil-off gases "BOG" from storages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
    • F25J1/0032—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration"
    • F25J1/0035—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration" by gas expansion with extraction of work
    • F25J1/0037—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration" by gas expansion with extraction of work of a return stream
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
    • F25J1/0032—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration"
    • F25J1/004—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration" by flash gas recovery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/003—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production
    • F25J1/0032—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration"
    • F25J1/0045—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures characterised by the kind of cold generation within the liquefaction unit for compensating heat leaks and liquid production using the feed stream itself or separated fractions from it, i.e. "internal refrigeration" by vaporising a liquid return stream
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0201—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process using only internal refrigeration means, i.e. without external refrigeration
    • F25J1/0202—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process using only internal refrigeration means, i.e. without external refrigeration in a quasi-closed internal refrigeration loop
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0228—Coupling of the liquefaction unit to other units or processes, so-called integrated processes
    • F25J1/0229—Integration with a unit for using hydrocarbons, e.g. consuming hydrocarbons as feed stock
    • F25J1/023—Integration with a unit for using hydrocarbons, e.g. consuming hydrocarbons as feed stock for the combustion as fuels, i.e. integration with the fuel gas system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
    • F25J1/0244—Operation; Control and regulation; Instrumentation
    • F25J1/0245—Different modes, i.e. 'runs', of operation; Process control
    • F25J1/0249—Controlling refrigerant inventory, i.e. composition or quantity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
    • F25J1/0257—Construction and layout of liquefaction equipments, e.g. valves, machines
    • F25J1/0275—Construction and layout of liquefaction equipments, e.g. valves, machines adapted for special use of the liquefaction unit, e.g. portable or transportable devices
    • F25J1/0277—Offshore use, e.g. during shipping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
    • F25J1/0279—Compression of refrigerant or internal recycle fluid, e.g. kind of compressor, accumulator, suction drum etc.
    • F25J1/0285—Combination of different types of drivers mechanically coupled to the same refrigerant compressor, possibly split on multiple compressor casings
    • F25J1/0288—Combination of different types of drivers mechanically coupled to the same refrigerant compressor, possibly split on multiple compressor casings using work extraction by mechanical coupling of compression and expansion of the refrigerant, so-called companders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J1/00—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures
    • F25J1/02—Processes or apparatus for liquefying or solidifying gases or gaseous mixtures requiring the use of refrigeration, e.g. of helium or hydrogen ; Details and kind of the refrigeration system used; Integration with other units or processes; Controlling aspects of the process
    • F25J1/0243—Start-up or control of the process; Details of the apparatus used; Details of the refrigerant compression system used
    • F25J1/0279—Compression of refrigerant or internal recycle fluid, e.g. kind of compressor, accumulator, suction drum etc.
    • F25J1/0294—Multiple compressor casings/strings in parallel, e.g. split arrangement
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63J—AUXILIARIES ON VESSELS
    • B63J99/00—Subject matter not provided for in other groups of this subclass
    • B63J2099/001—Burning of transported goods, e.g. fuel, boil-off or refuse
    • B63J2099/003—Burning of transported goods, e.g. fuel, boil-off or refuse of cargo oil or fuel, or of boil-off gases, e.g. for propulsive purposes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
    • F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
    • F02M21/0203—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels characterised by the type of gaseous fuel
    • F02M21/0215—Mixtures of gaseous fuels; Natural gas; Biogas; Mine gas; Landfill gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2221/00—Handled fluid, in particular type of fluid
    • F17C2221/03—Mixtures
    • F17C2221/032—Hydrocarbons
    • F17C2221/033—Methane, e.g. natural gas, CNG, LNG, GNL, GNC, PLNG
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2223/00—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel
    • F17C2223/01—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel characterised by the phase
    • F17C2223/0146—Two-phase
    • F17C2223/0153—Liquefied gas, e.g. LPG, GPL
    • F17C2223/0161—Liquefied gas, e.g. LPG, GPL cryogenic, e.g. LNG, GNL, PLNG
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2223/00—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel
    • F17C2223/03—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel characterised by the pressure level
    • F17C2223/033—Small pressure, e.g. for liquefied gas
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2227/00—Transfer of fluids, i.e. method or means for transferring the fluid; Heat exchange with the fluid
    • F17C2227/01—Propulsion of the fluid
    • F17C2227/0128—Propulsion of the fluid with pumps or compressors
    • F17C2227/0171—Arrangement
    • F17C2227/0185—Arrangement comprising several pumps or compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2227/00—Transfer of fluids, i.e. method or means for transferring the fluid; Heat exchange with the fluid
    • F17C2227/03—Heat exchange with the fluid
    • F17C2227/0337—Heat exchange with the fluid by cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2227/00—Transfer of fluids, i.e. method or means for transferring the fluid; Heat exchange with the fluid
    • F17C2227/03—Heat exchange with the fluid
    • F17C2227/0337—Heat exchange with the fluid by cooling
    • F17C2227/0339—Heat exchange with the fluid by cooling using the same fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2227/00—Transfer of fluids, i.e. method or means for transferring the fluid; Heat exchange with the fluid
    • F17C2227/03—Heat exchange with the fluid
    • F17C2227/0337—Heat exchange with the fluid by cooling
    • F17C2227/0358—Heat exchange with the fluid by cooling by expansion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2265/00—Effects achieved by gas storage or gas handling
    • F17C2265/01—Purifying the fluid
    • F17C2265/015—Purifying the fluid by separating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2265/00—Effects achieved by gas storage or gas handling
    • F17C2265/01—Purifying the fluid
    • F17C2265/015—Purifying the fluid by separating
    • F17C2265/017—Purifying the fluid by separating different phases of a same fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2265/00—Effects achieved by gas storage or gas handling
    • F17C2265/03—Treating the boil-off
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2265/00—Effects achieved by gas storage or gas handling
    • F17C2265/03—Treating the boil-off
    • F17C2265/032—Treating the boil-off by recovery
    • F17C2265/037—Treating the boil-off by recovery with pressurising
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2265/00—Effects achieved by gas storage or gas handling
    • F17C2265/06—Fluid distribution
    • F17C2265/066—Fluid distribution for feeding engines for propulsion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
    • F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
    • F17C2270/00—Applications
    • F17C2270/01—Applications for fluid transport or storage
    • F17C2270/0102—Applications for fluid transport or storage on or in the water
    • F17C2270/0105—Ships
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2290/00—Other details not covered by groups F25J2200/00 - F25J2280/00
    • F25J2290/72—Processing device is used off-shore, e.g. on a platform or floating on a ship or barge
    • 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
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/30—Use of alternative fuels, e.g. biofuels
    • 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
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T70/00—Maritime or waterways transport
    • Y02T70/50—Measures to reduce greenhouse gas emissions related to the propulsion system

Definitions

  • the present invention relates to a ship, and more particularly, to a ship including a system for re-liquefying the remaining boil-off gas used as the fuel of the engine in the boil-off gas generated inside the storage tank.
  • Liquefied gas liquefied gas at low temperature has the advantage that the storage and transport efficiency can be improved because the volume is very small compared to the gas.
  • liquefied gas, including liquefied natural gas can remove or reduce air pollutants during the liquefaction process, it can be seen as an environmentally friendly fuel with less emissions of air pollutants during combustion.
  • Liquefied natural gas is a colorless and transparent liquid obtained by liquefying natural gas containing methane as a main component at about -162 °C, and has a volume of about 1/600 compared with natural gas. Therefore, when liquefied and transported natural gas can be transported very efficiently.
  • the liquefaction temperature of natural gas is a cryogenic temperature of -162 °C
  • liquefied natural gas is easily evaporated because it is sensitive to temperature changes.
  • the storage tank storing the liquefied natural gas is insulated.
  • the natural gas is continuously vaporized in the storage tank during the transport of the liquefied natural gas.
  • -Off Gas, BOG occurs.
  • BOG -Off Gas
  • Boil-off gas is a kind of loss and is an important problem in transportation efficiency.
  • the internal pressure of the tank may be excessively increased, and there is also a risk that the tank may be damaged. Accordingly, various methods for treating the boil-off gas generated in the storage tank have been studied.
  • a method of re-liquefying the boil-off gas to return to the storage tank, and returning the boil-off gas to the fuel of a ship engine The method used as an energy source of a consumer is used.
  • a refrigeration cycle using a separate refrigerant is used to re-liquefy the boil-off gas by exchanging the boil-off gas with the refrigerant, and a method of re-liquefying the boil-off gas itself as a refrigerant without a separate refrigerant.
  • PRS Partial Re-liquefaction System
  • DFDE is composed of four strokes and adopts the Otto Cycle, which injects natural gas with a relatively low pressure of 6.5 bar into the combustion air inlet and compresses the piston as it rises.
  • the ME-GI engine is composed of two strokes and employs a diesel cycle that directly injects high pressure natural gas near 300 bar into the combustion chamber near the top dead center of the piston. Recently, there is a growing interest in ME-GI engines with better fuel efficiency and propulsion efficiency.
  • a ship including a storage tank for storing liquefied gas, it is installed downstream of the storage tank, compressed by the evaporated gas discharged from the storage tank as a refrigerant
  • An boil-off gas heat exchanger for cooling by boil-off heat of the boil-off gas (hereinafter referred to as 'first fluid');
  • a compressor installed downstream of the boil-off heat exchanger to compress a portion of the boil-off gas discharged from the storage tank;
  • a spare compressor installed downstream of the boil-off gas heat exchanger in parallel with the compressor to compress another portion of the boil-off gas discharged from the storage tank;
  • a refrigerant heat exchanger for further cooling the first fluid cooled by the evaporative gas heat exchanger;
  • a refrigerant pressure reducing device which is sent to the refrigerant heat exchanger (hereinafter, the fluid sent to the refrigerant heat exchanger is referred to as a 'second fluid'), and expands the second fluid cooled by the refrigerant heat
  • first fluid comprises: an evaporated gas compressed by the compressor; And a stream in which the boil-off gas compressed by the compressor and the boil-off gas compressed by the extra compressor are joined.
  • the second fluid may be any one of: an evaporated gas compressed by the extra compressor; And a stream in which the boil-off gas compressed by the compressor and the boil-off gas compressed by the extra compressor are joined. Any one of the vessels is provided.
  • the vessel may further include a gas-liquid separator for separating the partially liquefied liquefied gas and the evaporated gas remaining in the gaseous state through the boil-off gas heat exchanger, the refrigerant heat exchanger and the first decompression device,
  • the liquefied gas separated by the gas-liquid separator may be sent to the storage tank, and the boil-off gas separated by the gas-liquid separator may be sent to the boil-off gas heat exchanger.
  • the first fluid branches into two streams upstream of the fuel source, with a portion passing sequentially through the boil-off gas heat exchanger, the refrigerant heat exchanger, and the first depressurization device, and some or all of which may be reliquefied, Some may be sent to the fuel demand.
  • the second fluid used as the refrigerant of the refrigerant heat exchanger is again sent to the spare compressor, whereby the spare compressor and the refrigerant heat exchange
  • a refrigerant cycle of a closed loop connecting the refrigerant pressure reducing device to the refrigerant heat exchanger may be formed.
  • the second fluid used as the refrigerant of the refrigerant heat exchanger after being compressed by the redundant compressor and passed through the refrigerant heat exchanger and the refrigerant pressure reducing device passes through the evaporative gas heat exchanger after being discharged from the storage tank. It can be combined with the boil-off gas.
  • the vessel may further include a valve installed on a line for communicating the first fluid and the second fluid, wherein the valve is evaporated by the extra compressor and the evaporated gas compressed by the compressor. It can be opened and closed to join or separate gases.
  • the refrigerant reducing device may be an expander, and the fluid immediately before passing through the refrigerant reducing device and the fluid immediately after passing may be gaseous.
  • the boil-off gas treatment system including a storage tank for storing liquefied gas, after compressing a portion of the boil-off gas discharged from the storage tank by a compressor A first supply line for sending to fuel demand; A second supply line branched from the first supply line to compress another portion of the boil-off gas discharged from the storage tank by an extra compressor; A return line branched from the first supply line to reliquefy the compressed boil-off gas through an boil-off gas heat exchanger, a refrigerant heat exchanger, and a first pressure reducing device; A recirculation line passing through the refrigerant heat exchanger and the refrigerant pressure reducing device and sending the cooled boil-off gas back to the refrigerant heat exchanger for use as a refrigerant, and then joining the boil-off gas discharged from the storage tank; A first additional line connecting between the refrigerant reducing device and the recirculation line downstream of the refrigerant heat exchanger
  • the heat exchanger cools the evaporated gas supplied along the return line
  • the refrigerant heat exchanger comprises: an evaporated gas supplied along the recirculation line using the evaporated gas passed through the refrigerant reducing device as a refrigerant; And an evaporation gas supplied along the return line.
  • the vessel's boil-off gas treatment system includes: a first valve installed on the first supply line upstream of the compressor; A second valve installed on the first supply line downstream of the compressor; A third valve installed on the second supply line upstream of the redundant compressor; A fourth valve installed on the second supply line downstream of the redundant compressor; A fifth valve installed on the return line upstream of the boil-off gas heat exchanger; A sixth valve installed in the recirculation line upstream of the refrigerant pressure reducing device and the refrigerant heat exchanger; A ninth valve installed in the recirculation line downstream of the refrigerant reducing device and the refrigerant heat exchanger; A tenth valve installed on the first additional line; A twelfth valve installed on the second additional line; A thirteenth valve installed on the third additional line; A fourteenth valve installed on the fourth additional line; And a fifteenth valve installed on the fifth additional line.
  • the boil-off gas treatment system of the vessel may further include an eleventh valve installed on the first supply line upstream of the fuel demand and downstream of the second supply line.
  • the first valve, the second valve, the third valve, the fifth valve, the sixth valve, and the tenth valve are opened, and the fourth valve, the ninth valve, the twelfth valve, and the first valve are opened.
  • the thirteenth valve, the fourteenth valve, and the fifteenth valve operate the system in the closed state, and close the third valve when the boil-off gas is supplied to the spare compressor, so that the boil-off gas is supplied to the spare compressor, the sixth valve,
  • a closed loop refrigerant cycle may be formed to circulate the refrigerant heat exchanger, the refrigerant pressure reducing device, the refrigerant heat exchanger, and the tenth valve.
  • the first valve, the second valve, the fifth valve, the sixth valve, and the tenth valve are closed, and the third valve and the fourth valve are opened, and from the storage tank.
  • the boil-off gas passing through the boil-off gas heat exchanger may be supplied to the fuel demand via the third valve, the spare compressor, and the fourth valve.
  • the first valve, the third valve, the fourth valve, the twelfth valve, the fourteenth valve, and the fifteenth valve are opened, and the second valve, the fifth valve, the sixth valve, and the fifth valve are opened.
  • the ninth valve, the tenth valve, and the thirteenth valve drive the system in a closed state, and when the boil-off gas is supplied to the compressor, close the first valve so that the boil-off gas is placed on the compressor, the fourteenth valve, the A closed loop refrigerant cycle circulating through the refrigerant heat exchanger, the refrigerant pressure reducing device, the refrigerant heat exchanger, and the twelfth valve may be formed.
  • the third valve, the fourth valve, the twelfth valve, the fourteenth valve, and the fifteenth valve are closed, and the first valve and the second valve are opened to open the storage tank.
  • the boil-off gas passing through the boil-off gas heat exchanger may be supplied to the fuel demand via the first valve, the compressor, and the second valve.
  • the first valve, the second valve, the third valve, the fifth valve, the sixth valve, the ninth valve, and the thirteenth valve are opened, and the fourth valve, the tenth valve, and the fifth valve are opened.
  • the twelve valve, the fourteenth valve, and the fifteenth valve are closed to operate by combining the boil-off gas compressed by the compressor and the boil-off gas compressed by the spare compressor.
  • the third valve is closed by closing the first valve, the fifth valve, the sixth valve, and the ninth valve, and having passed through the boil-off gas heat exchanger after being discharged from the storage tank.
  • the valve may be supplied to the fuel demand via the spare compressor, the thirteenth valve, and the second valve.
  • the first valve, the second valve, the third valve, the fifth valve, the sixth valve, and the ninth valve are opened, and the fourth valve, the tenth valve, the twelfth valve, and the ninth valve are opened.
  • the thirteenth valve, the fourteenth valve, and the fifteenth valve may be closed to separate and operate the boil-off gas compressed by the compressor and the boil-off gas compressed by the spare compressor.
  • the first valve, the fifth valve, the sixth valve, and the ninth valve are closed, the thirteenth valve is opened, and discharged from the storage tank to pass through the evaporative gas heat exchanger.
  • the boil-off gas may be supplied to the fuel demand via the third valve, the spare compressor, the thirteenth valve, and the second valve.
  • the compressor downstream line and the extra compressor downstream line may be connected so that the boil-off gas compressed by the compressor may be combined with the boil-off gas compressed by the extra compressor.
  • a ship including a storage tank for storing liquefied gas, is installed downstream of the storage tank, compressed by the evaporated gas discharged from the storage tank as a refrigerant
  • An evaporating gas heat exchanger configured to cool the evaporated gas (hereinafter, referred to as “first fluid”) by heat exchange;
  • a compressor installed downstream of the boil-off heat exchanger to compress a portion of the boil-off gas discharged from the storage tank;
  • a first spare compressor installed downstream of the boil-off gas heat exchanger in parallel with the compressor to compress another portion of the boil-off gas discharged from the storage tank;
  • a second spare compressor installed downstream of the boil-off gas heat exchanger in parallel with the compressor and the first spare compressor to compress the remaining part of the boil-off gas discharged from the storage tank;
  • a refrigerant heat exchanger for further cooling the first fluid cooled by the evaporative gas heat exchanger;
  • a refrigerant pressure reducing device which is sent to the refrigerant heat exchanger (hereinafter
  • the refrigerant heat exchanger uses the evaporated gas passed through the refrigerant reducing device as a refrigerant, Heat-exchanging both the first fluid and the second fluid
  • the first fluid comprises: an evaporated gas compressed by the compressor; An evaporated gas compressed by the first extra compressor; A flow in which the boil-off gas compressed by the compressor and the boil-off gas compressed by the first extra compressor are joined; And a stream in which the boil-off gas compressed by the compressor, the boil-off gas compressed by the first spare compressor, and the boil-off gas compressed by the second spare compressor are joined.
  • the second fluid may be any one of: an evaporated gas compressed by the first extra compressor; Boil-off gas compressed by the second extra compressor; A flow in which the boil-off gas compressed by the first extra compressor and the boil-off gas compressed by the second extra compressor are joined; And a stream in which the boil-off gas compressed by the compressor, the boil-off gas compressed by the first spare compressor, and the boil-off gas compressed by the second spare compressor are joined. Any one of the vessels is provided.
  • the evaporated gas used as the refrigerant of the refrigerant heat exchanger after passing through the refrigerant pressure reducing device may be combined with the evaporated gas passed through the evaporation gas heat exchanger after being discharged from the storage tank.
  • the boil-off gas used as the refrigerant of the refrigerant heat exchanger after being compressed by the first spare compressor is sent to the first spare compressor again, so that the first spare compressor, the refrigerant heat exchanger, the refrigerant pressure reducing device, and the refrigerant heat exchange again.
  • a closed loop refrigerant cycle can be formed that circulates the groups.
  • the evaporated gas used as the refrigerant of the refrigerant heat exchanger after being compressed by the second spare compressor is sent to the second spare compressor again, so that the second spare compressor, the refrigerant heat exchanger, the refrigerant pressure reducing device, and the refrigerant heat exchange again.
  • a closed loop refrigerant cycle can be formed that circulates the groups.
  • the boil-off gas compressed by the first spare compressor and the boil-off gas compressed by the second spare compressor are combined and supplied to the refrigerant heat exchanger, and the boil-off gas supplied to the refrigerant heat exchanger is the refrigerant reducing device. After passing through the refrigerant heat exchanger, it may branch back into two flows to form a closed loop refrigerant cycle that is sent to the first or second redundant compressor.
  • the ship boil-off gas treatment system including a storage tank for storing liquefied gas, a portion of the boil-off gas discharged from the storage tank is compressed by a compressor A first supply line which is then sent to the fuel demand; A second supply line branched from the first supply line and compressing another portion of the boil-off gas discharged from the storage tank by a first spare compressor; A third supply line branched from the second supply line to compress the remaining portion of the boil-off gas discharged from the storage tank by a second extra compressor; A return line branched from the first supply line to reliquefy the compressed boil-off gas through an boil-off gas heat exchanger, a refrigerant heat exchanger, and a first pressure reducing device; And a recirculation line passing through the refrigerant heat exchanger and the refrigerant decompression device and sending the cooled boil-off gas back to the refrigerant heat exchanger for use as a refrigerant, and then
  • the gas heat exchanger uses the evaporated gas discharged from the storage tank as a refrigerant, and heats and cools the evaporated gas supplied along the return line, and the refrigerant heat exchanger uses the evaporated gas passed through the refrigerant pressure reducing device as a refrigerant. , Boil-off gas supplied along the recycle line; And an evaporation gas supplied along the return line.
  • the recirculation line upstream of the refrigerant reducing device and the refrigerant heat exchanger comprises: the third supply line downstream of the second redundant compressor; And the second supply line downstream of the first extra compressor; may be sequentially connected to the first supply line downstream of the compressor, and the boil-off gas treatment system of the vessel may be connected to the first supply line on the first supply line.
  • the vessel's boil-off gas treatment system includes: a first additional line connecting between the recycle line and the third supply line; A second additional line connecting between the first additional line and the second supply line; A thirteenth valve installed on the first additional line; And a fourteenth valve installed on the second additional line.
  • One side of the first additional line may be connected to the recirculation line which sends the boil-off gas passing through the refrigerant pressure reducing device and the refrigerant heat exchanger to the first supply line, and the other side of the first additional line includes the tenth valve and the second spare. It may be connected to the third supply line between the compressor, one side of the second additional line, may be connected to the first additional line upstream of the thirteenth valve, the other side, the third valve and the first redundant It can be connected to said second supply line between compressors.
  • any one of the compressor, the first spare compressor, and the second spare compressor may be used.
  • the compressor, the first spare compressor, And any two of the second spare compressors, and when the vessel is anchored, all of the compressor, the first spare compressor, and the second spare compressor can be used.
  • the ninth valve, the twelfth valve and the fourteenth valve operate the system in a closed state, and when the boil-off gas is supplied to the second spare compressor, the tenth valve is closed so that the boil-off gas is supplied to the second spare compressor,
  • a closed loop refrigerant cycle may be formed to circulate the eleventh valve, the refrigerant heat exchanger, the refrigerant pressure reducing device, the refrigerant heat exchanger, and the thirteenth valve.
  • the first valve, the second valve, the third valve, the fourth valve, the twelfth valve, the fourteenth valve, and the fifteenth valve are opened, and the sixth valve, the ninth valve, and the fifth valve are opened.
  • the tenth valve, the eleventh valve, and the thirteenth valve operate the system in a closed state, and when the boil-off gas is supplied to the first spare compressor, the third valve is closed so that the boil-off gas is supplied to the first spare compressor,
  • a closed loop refrigerant cycle may be formed to circulate the fourth valve, the twelfth valve, the refrigerant heat exchanger, the refrigerant pressure reducing device, the refrigerant heat exchanger, and the fourteenth valve.
  • the three valves, the sixth valve, and the tenth valve drive the system in the closed state, and when the boil-off gas is supplied to the first extra compressor and the second extra compressor, the ninth valve is closed to close the first valve.
  • the boil-off gas compressed by the spare compressor and the boil-off gas passing through the second spare compressor are combined and supplied to the refrigerant heat exchanger, and the boil-off gas supplied to the refrigerant heat exchanger passes through the refrigerant pressure reducing device and again the refrigerant heat exchanger. It is then branched back into two flows to form a closed loop refrigerant cycle that is sent to the first and second spare compressors, respectively.
  • the first valve, the second valve, the third valve, the fourth valve, the sixth valve, the ninth valve, the tenth valve, the eleventh valve, the twelfth valve, and the fifteenth valve Is opened, the thirteenth valve and the fourteenth valve are closed, and the boil-off gas compressed by the compressor, the boil-off gas compressed by the first spare compressor, and the boil-off gas compressed by the second spare compressor are joined. Can be operated.
  • the sixth valve, the thirteenth valve, and the fourteenth valve are closed, and the boil-off gas compressed by the first spare compressor and the boil-off gas compressed by the second spare compressor are combined and sent to the refrigerant heat exchanger.
  • the compressed boil-off gas may be sent to the fuel demand, and some to the boil-off heat exchanger.
  • the twelve valve, the thirteenth valve, and the fourteenth valve are closed, and the boil-off gas compressed by the second spare compressor is sent to the refrigerant heat exchanger, and the boil-off gas compressed by the compressor and the first spare compressor are
  • the compressed boil-off gas can be combined to send some to fuel demand and the other to the boil-off heat exchanger.
  • the compressor downstream line and the first extra compressor downstream line may be connected so that the boil-off gas compressed by the compressor may be combined with the boil-off gas compressed by the first extra compressor.
  • the first spare compressor downstream line and the second spare compressor downstream line may be connected so that the boil-off gas compressed by the first spare compressor may be combined with the boil-off gas compressed by the second spare compressor.
  • An evaporation gas compressed by the compressor by connecting the compressor downstream line, the first extra compressor downstream line, and the second extra compressor downstream line; An evaporated gas compressed by the first extra compressor; And a boil-off gas compressed by the second extra compressor.
  • a ship including a storage tank for storing liquefied gas, is installed downstream of the storage tank, compressed by the evaporated gas discharged from the storage tank as a refrigerant
  • An evaporating gas heat exchanger configured to cool the evaporated gas (hereinafter, referred to as “first fluid”) by heat exchange;
  • a compressor installed downstream of the boil-off heat exchanger to compress a portion of the boil-off gas discharged from the storage tank;
  • a spare compressor installed downstream of the boil-off gas heat exchanger in parallel with the compressor to compress another portion of the boil-off gas discharged from the storage tank;
  • a propelling compressor installed upstream of the boil-off gas heat exchanger to compress the first fluid supplied to the boil-off gas heat exchanger;
  • a refrigerant heat exchanger for further cooling the first fluid cooled by the evaporative gas heat exchanger;
  • a refrigerant pressure reducing device which is sent to the refrigerant heat exchanger (hereinafter, the fluid sent to the refrigerant heat exchange
  • first fluid comprises: an evaporated gas compressed by the compressor; And a stream in which the boil-off gas compressed by the compressor and the boil-off gas compressed by the extra compressor are joined.
  • the second fluid may be any one of: an evaporated gas compressed by the extra compressor; And a stream in which the boil-off gas compressed by the compressor and the boil-off gas compressed by the extra compressor are joined. Any one of the vessels is provided.
  • the vessel may further include a gas-liquid separator for separating the partially liquefied liquefied gas and the evaporated gas remaining in the gaseous state through the boil-off gas heat exchanger, the refrigerant heat exchanger and the first decompression device,
  • the liquefied gas separated by the gas-liquid separator may be sent to the storage tank, and the boil-off gas separated by the gas-liquid separator may be sent to the boil-off gas heat exchanger.
  • the propulsion compressor may have a capacity of 1/2 of the compressor.
  • the first fluid branches into two streams upstream of the fuel demand, with a portion passing sequentially through the propulsion compressor, the boil-off gas heat exchanger, the refrigerant heat exchanger, and the first depressurization device and part or all of which is to be liquefied. And some may be sent to the fuel demand.
  • the second fluid used as the refrigerant of the refrigerant heat exchanger is again sent to the spare compressor, whereby the spare compressor and the refrigerant heat exchange
  • a refrigerant cycle of a closed loop connecting the refrigerant pressure reducing device to the refrigerant heat exchanger may be formed.
  • the second fluid used as the refrigerant of the refrigerant heat exchanger after being compressed by the redundant compressor and passed through the refrigerant heat exchanger and the refrigerant pressure reducing device passes through the evaporative gas heat exchanger after being discharged from the storage tank. It can be combined with the boil-off gas.
  • the vessel may further include a valve installed on a line for communicating the first fluid and the second fluid, wherein the valve is evaporated by the extra compressor and the evaporated gas compressed by the compressor. It can be opened and closed to join or separate gases.
  • the propulsion compressor may compress the boil-off gas to a pressure below a critical point.
  • the propulsion compressor may compress the boil-off gas to a pressure exceeding a critical point.
  • the propulsion compressor may compress the boil-off gas to 300 bar.
  • the ship boil-off gas treatment system including a storage tank for storing liquefied gas, a portion of the boil-off gas discharged from the storage tank is compressed by a compressor A first supply line which is then sent to the fuel demand; A second supply line branched from the first supply line to compress another portion of the boil-off gas discharged from the storage tank by an extra compressor; A return line branched from the first supply line to reliquefy the compressed boil-off gas through a propulsion compressor, a boil-off gas heat exchanger, a refrigerant heat exchanger, and a first pressure reducing device; And a recirculation line passing through the refrigerant heat exchanger and the refrigerant decompression device and sending the cooled boil-off gas back to the refrigerant heat exchanger for use as a refrigerant, and then joining the boil-off gas discharged from the storage tank.
  • the gas heat exchanger uses the evaporated gas discharged from the storage tank as a refrigerant, and heats and cools the evaporated gas supplied along the return line, and the refrigerant heat exchanger uses the evaporated gas passed through the refrigerant pressure reducing device as a refrigerant. , Boil-off gas supplied along the recycle line; And an evaporation gas supplied along the return line.
  • the boil-off gas treatment system includes: a first valve installed upstream of the compressor on the first supply line; A second valve installed downstream of the compressor on the first supply line; A third valve installed upstream of the redundant compressor on the second supply line; A fourth valve installed downstream of the redundant compressor on the second supply line; A sixth valve installed between the first supply line and the second supply line of the recirculation line that sends the evaporated gas branched from the first supply line to the refrigerant heat exchanger; A ninth valve installed on the recirculation line for sending boil-off gas from the refrigerant heat exchanger to the first supply line; A first additional line connecting the recirculation line between the ninth valve and the refrigerant heat exchanger and the second supply line between the third valve and the spare compressor; And a tenth valve installed on the first additional line.
  • the first valve, the second valve, the third valve, the fourth valve, and the tenth valve are opened, the sixth valve and the ninth valve are closed to drive the system, and the evaporation gas is
  • the third valve is closed so that evaporated gas is circulated through the spare compressor, the fourth valve, the refrigerant heat exchanger, the refrigerant pressure reducing device, the refrigerant heat exchanger, and the tenth valve.
  • the refrigerant cycle of the loop can be formed.
  • the first valve, the second valve and the tenth valve are closed, the third valve and the sixth valve are opened, and the evaporation passed through the evaporative gas heat exchanger after being discharged from the storage tank.
  • the gas may be supplied to the fuel demand via the third valve, the spare compressor, the fourth valve, and the sixth valve.
  • the first valve, the second valve, the third valve, the fourth valve, the sixth valve, and the ninth valve are opened, and the tenth valve is closed, and the evaporated gas and the redundant gas compressed by the compressor are closed.
  • the boil-off gas compressed by the compressor may be combined and operated.
  • the first valve and the second valve are closed to allow the boil-off gas passed through the boil-off gas heat exchanger after being discharged from the storage tank to the third valve, the spare compressor, the fourth valve and Via the sixth valve may be supplied to the fuel demand.
  • the first valve, the second valve, the third valve, the fourth valve and the ninth valve are opened, the sixth valve and the tenth valve are closed, and the evaporated gas compressed by the compressor and the redundant
  • the boil-off gas compressed by the compressor may be separated and operated.
  • the first valve and the second valve are closed, the sixth valve is opened, and the boil-off gas passed through the boil-off gas heat exchanger after being discharged from the storage tank is stored in the third valve, the excess.
  • the fourth valve and the sixth valve may be supplied to the fuel demand.
  • the compressor downstream line and the extra compressor downstream line may be connected so that the boil-off gas compressed by the compressor may be combined with the boil-off gas compressed by the extra compressor.
  • the present invention can increase the reliquefaction efficiency and the amount of reliquefaction since the evaporated gas is decompressed after the additional cooling process by the refrigerant heat exchanger.
  • it is economical to re-liquefy most or all of the remaining boil-off gas without using a refrigeration cycle using a separate refrigerant.
  • the re-liquefaction efficiency and the amount of reliquefaction are increased by using the spare compressor that is already installed, it contributes to securing the space on board and further reduces the cost of installing the compressor.
  • not only the boil-off gas compressed by the spare compressor but also the boil-off gas compressed by the compressor can be used as the refrigerant in the refrigerant heat exchanger, thereby increasing the flow rate of the boil-off gas used as the refrigerant in the refrigerant heat exchanger. It is possible to further increase the liquefaction efficiency and the amount of reliquefaction.
  • the propulsion compressor further includes, since it is possible to increase the pressure of the boil-off gas undergoing the reliquefaction process, it is possible to further increase the reliquefaction efficiency and reliquefaction amount.
  • FIG. 1 is a schematic view showing a conventional partial reliquefaction system.
  • Figure 2 is a schematic diagram showing a boil-off gas treatment system according to a first embodiment of the present invention.
  • FIG. 3 is a configuration diagram schematically showing a boil-off gas treatment system according to a second embodiment of the present invention.
  • FIG. 4 is a configuration diagram schematically showing a system for treating boil-off gas in accordance with a third embodiment of the present invention.
  • FIG. 5 is a configuration diagram schematically showing a boil-off gas treatment system according to a fourth embodiment of the present invention.
  • Figure 6 is a schematic diagram showing a system for treating the boil-off gas in accordance with a fifth embodiment of the present invention.
  • FIG. 7 is a configuration diagram schematically showing a boil-off gas treatment system according to a sixth embodiment of the present invention.
  • FIG. 8 is a configuration diagram schematically showing a boil-off gas treatment system according to a seventh embodiment of the present invention.
  • 9 is a graph schematically illustrating a phase change of methane according to temperature and pressure.
  • 10 is a graph showing the temperature value of methane according to the heat flow amount under different pressure, respectively.
  • the vessel of the present invention can be applied to various applications, such as a vessel equipped with an engine using natural gas as a fuel, and a vessel including a liquefied gas storage tank.
  • a vessel equipped with an engine using natural gas as a fuel and a vessel including a liquefied gas storage tank.
  • the following examples may be modified in many different forms, and the scope of the present invention is not limited to the following examples.
  • the system for the treatment of boil-off gas to be described later of the present invention includes all kinds of vessels and offshore structures, that is, liquefied natural gas carriers, liquefied ethane gas carriers, equipped with storage tanks capable of storing low temperature liquid cargo or liquefied gas, It can be applied to ships such as LNG RV, as well as offshore structures such as LNG FPSO, LNG FSRU.
  • LNG RV liquefied natural gas carriers
  • LNG FPSO liquefied ethane gas carriers
  • the fluid in each line of the present invention may be in any one of a liquid state, a gas-liquid mixed state, a gas state, and a supercritical fluid state, depending on the operating conditions of the system.
  • FIG. 1 is a schematic view showing a conventional partial reliquefaction system.
  • the boil-off gas generated and discharged from the storage tank for storing the liquid cargo is transferred along the pipe and compressed in the boil-off gas compression unit 10.
  • the storage tank (T) has a sealing and insulation barrier to store liquefied gas such as liquefied natural gas in a cryogenic state, but it cannot completely block the heat transmitted from the outside, and the liquefied gas evaporates continuously in the tank.
  • the internal pressure of the tank may be increased, and to prevent excessive increase in the tank pressure due to the boil-off gas, and to discharge the boil-off gas inside the storage tank to maintain an appropriate level of internal pressure, the boil-off gas compression unit 10 may be used. Supply.
  • the boil-off gas discharged from the storage tank and compressed in the boil-off gas compression unit 10 is called a first stream
  • the first stream of compressed boil-off gas is divided into a second stream and a third stream
  • the second stream is liquefied. It is configured to return to the storage tank (T), and the third stream can be configured to supply to a gas fuel consumer such as a propulsion engine or a power generation engine on board.
  • the boil-off gas compression unit 10 may compress the boil-off gas to the supply pressure of the fuel consumer, and the second stream may branch through all or part of the boil-off gas compression unit as necessary.
  • all of the compressed boil-off gas may be supplied to the third stream, or all of the compressed boil-off gas may be supplied to the second stream to return the compressed boil-off gas to the storage tank.
  • Gas fuel consumption sources include high pressure gas injection engines (eg, ME-GI engines developed by MDT) and low pressure gas injection engines (eg, Wartsila's Generation X-Dual Fuel engine). ), DF Generator, gas turbine, DFDE and the like.
  • the heat exchanger 20 is installed to liquefy the second stream of compressed boil-off gas, and the boil-off gas generated from the storage tank is used as a cold heat source of the compressed boil-off gas.
  • the compressed boil-off gas, ie, the second stream, which has risen in temperature during the compression in the boil-off gas compression unit while passing through the heat exchanger 20 is cooled, and the boil-off gas generated in the storage tank and introduced into the heat exchanger 20 is heated. And is supplied to the boil-off gas compression unit 10.
  • the second stream of compressed boil-off gas may be supplied with cold heat from the boil-off gas before being compressed to at least partially liquefy.
  • the heat exchanger heat-exchanges the low-temperature evaporated gas immediately after being discharged from the storage tank and the high-pressure evaporated gas compressed by the evaporated gas compression unit to liquefy the high-pressure evaporated gas.
  • the boil-off gas of the second stream passing through the heat exchanger 20 is further cooled while being decompressed while passing through expansion means 30 such as an expansion valve or expander, and is supplied to the gas-liquid separator 40.
  • expansion means 30 such as an expansion valve or expander
  • the liquefied boil-off gas is separated from the gas and the liquid component in the gas-liquid separator, and the liquid component, that is, the liquefied natural gas, is returned to the storage tank, and the gas component, that is, the boil-off gas, is discharged from the storage tank so as to exchange the heat exchanger 20 and the boil-off gas.
  • the evaporation gas flow supplied to the compression unit 10 is joined to the evaporation gas flow, or supplied to the heat exchanger 20 and used as a cold heat source for heat-exchanging the high-pressure evaporation gas compressed by the evaporation gas compression unit 10. May be Of course, it may be sent to a gas combustion unit (GCU) or the like for combustion, or may be sent to a gas consumer (including a gas engine) for consumption.
  • GCU gas combustion unit
  • Another expansion means 50 may be further installed to further depressurize the gas separated in the gas-liquid separator before joining the boil-off gas stream.
  • Figure 2 is a schematic diagram showing a boil-off gas treatment system according to a first embodiment of the present invention.
  • the system of the present embodiment is characterized in that the refrigerant circulation section 300a for receiving the boil off gas generated from the low temperature liquid cargo stored in the storage tank to circulate the boil off gas to the refrigerant .
  • a refrigerant supply line for supplying the boil-off gas from the storage tank to the refrigerant circulation unit 300a
  • the valve supply line is provided with a valve 400a, a sufficient amount of evaporation gas to circulate the refrigerant circulation unit
  • the refrigerant circulation unit 300a is operated in a closed loop (closed loop).
  • a compressor 100a for compressing the boil-off gas generated from the low temperature liquid cargo of the storage tank T is provided.
  • the boil-off gas generated in the storage tank is introduced into the compressor 100a along the boil-off gas supply line BLa.
  • the storage tank T of the present embodiments may be made of an independent type tank in which the load of liquid cargo is not directly applied to the insulation layer, or a membrane type tank in which the load of cargo is directly applied to the insulation layer. Can be.
  • independent tank type tanks it is also possible to use a pressure vessel designed to withstand pressures of 2 barg or more.
  • the boil-off gas compressed by the compressor may be supplied as a fuel to a fuel demand including a propulsion engine and a power generation engine of a ship or offshore structure.
  • a fuel demand including a propulsion engine and a power generation engine of a ship or offshore structure.
  • the fuel consumption can consume the entire amount of boil-off gas, there may be no boil-off gas to be reliquefied.
  • the gaseous fuel consumption is low or absent, such as when the ship is anchored, the entire amount of the boil-off gas may be supplied to the reliquefaction line RLa.
  • the compressed boil-off gas is supplied to the boil-off gas heat exchanger 200a along the boil-off gas reliquefaction line RLa, and the boil-off gas heat exchanger 200a is the boil-off gas reliquefaction line RLa and the boil-off gas supply line BLa. It is provided over, and heat exchanges the boil-off gas to be introduced into the compressor (100a) and the boil-off gas compressed through at least a portion of the compressor.
  • the boil-off gas whose temperature is increased in the compression process is cooled by heat exchange with the low-temperature boil-off gas generated in the storage tank and introduced into the compressor 100a.
  • a refrigerant heat exchanger 500a is provided downstream of the boil-off gas heat exchanger 200a, and the boil-off gas heat-exchanged in the boil-off gas heat exchanger after compression is further cooled through heat exchange with the boil-off gas circulating in the refrigerant circulation unit 300a. .
  • the refrigerant circulation unit 300a is configured to reduce the refrigerant compressor 310a for compressing the evaporated gas supplied from the storage tank, the cooler 320a for cooling the evaporated gas compressed by the refrigerant compressor, and reduce the evaporated gas cooled in the cooler. It further comprises a refrigerant pressure reducing device (330a) for additional cooling.
  • the refrigerant decompression device 330a may be an expansion valve or an expander that adiabatically expands and cools the boil-off gas.
  • the evaporated gas cooled through the refrigerant pressure reducing device 330a is supplied to the refrigerant heat exchanger 500a as a refrigerant along the refrigerant circulation line CCLa, and is supplied from the refrigerant heat exchanger 500a through the evaporation gas heat exchanger 200a.
  • the boil-off gas is cooled through heat exchange with the boil-off gas.
  • the evaporated gas of the refrigerant circulation line CCLa passing through the refrigerant heat exchanger 500a is circulated to the refrigerant compressor 310a to circulate through the refrigerant circulation line while undergoing the above-described compression and cooling process.
  • the boil-off gas of the boil-off gas reliquefaction line RLa cooled in the refrigerant heat exchanger 500a is reduced in pressure through the first pressure reducing device 600a.
  • the first pressure reducing device 600a may be an expansion valve such as a Joule-Thomson valve or an expander.
  • the pressurized boil-off gas is supplied to the gas-liquid separator 700a downstream of the first decompression device 600a and gas-liquid separated, and the liquid separated from the gas-liquid separator 700a, that is, liquefied natural gas, is supplied to the storage tank T. Restored.
  • the gas separated from the gas-liquid separator 700a ie, the boil-off gas
  • It may be used as a cold heat source that joins the gas stream or is supplied to the boil-off gas heat exchanger 200a to heat-exchange the boil-off gas under high pressure compressed by the compressor 100a.
  • it may be sent to a gas combustion unit (GCU) for combustion, or may be sent to a fuel demand (including a gas engine) for consumption.
  • GCU gas combustion unit
  • FIG. 3 is a configuration diagram schematically showing a boil-off gas treatment system according to a second embodiment of the present invention.
  • the present embodiment cools the evaporated gas to be introduced into the refrigerant reducing device 330b from the cooler 320b in the refrigerant circulation unit 300b by heat exchange with the evaporated gas decompressed in the refrigerant reducing device 330b. After supplying to the refrigerant pressure reducing device (330b) is configured.
  • the evaporation gas downstream of the refrigerant decompression device is lower in temperature than the evaporation gas upstream of the refrigerant decompression device.
  • the boil-off gas upstream of the refrigerant reducing device 330b may be supplied to the refrigerant heat exchanger 500b (part A of FIG. 3). If necessary, a separate heat exchanger may be further configured to exchange heat with the boil-off gas upstream and downstream of the refrigerant pressure reducing device.
  • the system of the embodiments may re-liquefy and store the evaporated gas generated from the storage tank liquid cargo, thereby increasing the transport rate of the liquid cargo.
  • the gas compression unit GCU
  • GCU gas combustion unit
  • FIG. 4 is a configuration diagram schematically showing a system for treating boil-off gas in accordance with a third embodiment of the present invention.
  • the evaporation gas heat exchanger 110 is installed downstream of the storage tank (T); A compressor 120 and a spare compressor 122 installed downstream of the boil-off gas heat exchanger 110 to compress the boil-off gas discharged from the storage tank T; A cooler 130 for lowering the temperature of the boil-off gas compressed by the compressor 120; An extra cooler 132 for lowering the temperature of the boil-off gas compressed by the extra compressor 122; A first valve 191 installed upstream of the compressor 120; A second valve 192 installed downstream of the cooler 130; A third valve 193 installed upstream of the spare compressor 122; A fourth valve 194 installed downstream of the extra cooler 132; A refrigerant heat exchanger (140) for further cooling the boil-off gas cooled by the boil-off gas heat exchanger (110); A refrigerant pressure reducing device (160) which expands the evaporated gas passing through the refrigerant heat exchanger (140) and sends it back to the refrigerant heat exchanger (140); And a first pressure reducing
  • the boil-off gas naturally generated in the storage tank T and then discharged is supplied to the fuel demand 180 along the first supply line L1.
  • the boil-off gas heat exchanger 110 is installed in the first supply line (L1) to recover cold heat from the boil-off gas immediately after being discharged from the storage tank (T).
  • the vessel of the present embodiment may further include an eleventh valve 203 installed upstream of the fuel demand unit 180 to control the flow rate and opening and closing of the boil-off gas sent to the fuel demand unit 180.
  • the boil-off gas heat exchanger 110 receives the boil-off gas discharged from the storage tank T, and uses the boil-off gas to cool the boil-off gas supplied to the boil-off gas heat exchanger 110 along the return line L3.
  • a fifth valve 195 may be installed on the return line L3 to control the flow rate and opening and closing of the boil-off gas.
  • the compressor 120 and the spare compressor 122 compress the boil-off gas passed through the boil-off gas heat exchanger 110.
  • the compressor 120 is installed on the first supply line L1
  • the spare compressor 122 is installed on the second supply line L2.
  • the second supply line L2 branches from the first supply line L1 upstream of the compressor 120 and is connected to the first supply line L1 downstream of the compressor 120.
  • the compressor 120 and the spare compressor 122 may be installed in parallel, and may be a compressor having the same performance.
  • an additional compressor 122 and an extra cooler 132 are additionally installed in a ship in preparation for a failure of the compressor 120 and the cooler 130.
  • the extra compressor 122 and the extra cooler 132 are not used in the usual case in which the compressor 120 or the cooler 130 is not broken.
  • the third valve 193 upstream of the spare compressor 122 and the fourth valve 194 downstream of the spare cooler 132 are closed.
  • the compressor 120 or the cooler 130 is broken and the compressor 120 or the cooler 130 is broken, the third valve upstream of the spare compressor 122 may be supplied to the boil-off gas through the compressor 120 and the cooler 130.
  • the fourth valve 194 downstream of the 193 and the extra cooler 132 is opened, and the first valve 191 upstream of the compressor 120 and the second valve 192 downstream of the cooler 130 are closed to remove the boil-off gas. Is passed through the extra compressor 122 and the extra cooler 132 to be supplied to the fuel demand (180).
  • the present invention is to increase the re-liquefaction efficiency and the amount of re-liquefaction of the boil-off gas by using the extra compressor 122 and the extra cooler 132, which has not been used in the prior art, by the extra compressor 122
  • the compressed boil-off gas is sent to the fuel demand unit 180, and the other portion is used as a refrigerant to further cool the boil-off gas in the refrigerant heat exchanger 140.
  • the methane is in a supercritical fluid state at a temperature of about ⁇ 80 ° C. or more and a pressure of about 55 bar or more. That is, in the case of methane, the critical point is about -80 °C, 55bar state.
  • the supercritical fluid state is a third state different from the liquid state or the gas state.
  • the boil-off gas compressed by the compressor 120 or the extra compressor 122 may be in a gaseous state or a supercritical fluid state depending on the degree of compression.
  • the boil-off gas sent to the boil-off gas heat exchanger 110 through the return line L3 is in a gaseous state
  • the boil-off gas passes through the boil-off gas heat exchanger 110 and the temperature is lowered to become a mixed state of liquid and gas.
  • the temperature may be lowered while passing through the boil-off gas heat exchanger 110 to become a “high pressure liquid state”.
  • the boil-off gas cooled by the boil-off gas heat exchanger 110 has a lower temperature while passing through the coolant heat exchanger 140.
  • the boil-off gas passing through the boil-off gas heat exchanger 110 is a mixed state of liquid and gas.
  • the evaporated gas passes through the refrigerant heat exchanger 140, and the temperature is lowered so that the proportion of the liquid becomes a mixed state or becomes a liquid state.
  • the refrigerant heat exchanger 140 The temperature will be lower as it passes through.
  • the boil-off gas passing through the refrigerant heat exchanger 140 is a "high-pressure liquid state"
  • the boil-off gas passes through the first decompression device 150 to lower the pressure to become a liquid state or a mixed state of liquid and gas. do.
  • the boil-off gas is lowered to the same degree (P in FIG. 9) by the first decompression device 150, the temperature is lower than that in the case where the temperature is lowered (X ⁇ X 'in FIG. 9). It can be seen that when the pressure is reduced in the state (Y ⁇ Y ′ in FIG. 9), the proportion of the liquid becomes a higher mixed state. In addition, it can be seen that if the temperature can be further lowered, theoretically 100% of the evaporated gas can be reliquefied (Z ⁇ Z ′ in FIG. 9). Therefore, if the boil-off gas is further cooled by the refrigerant heat exchanger 140 before passing through the first pressure reducing device 150, the re-liquefaction efficiency and the amount of re-liquefaction may be increased.
  • the present embodiment compares the refrigerant cycles 300a and 300b for additionally cooling the boil-off gas in the first and second embodiments to form a closed loop.
  • the difference is that it consists of a loop.
  • the refrigerant circulation parts 300a and 300b are configured as closed loops, and the boil-off gas compressed by the refrigerant compressors 310a and 310b is transferred from the refrigerant heat exchangers 500a and 500b to the refrigerant. It is used only, and cannot be sent to fuel demand or undergo reliquefaction.
  • the refrigerant cycle is configured as an open loop, and after the boil-off gas compressed by the extra compressor 122 joins the boil-off gas compressed by the compressor 120, a part of the boil-off boiled gas is fueled. It is sent to the customer (180), the other part is used as the refrigerant heat exchanger 140 refrigerant along the recirculation line (L5), the other part is subjected to the reliquefaction process along the return line (L3).
  • the recirculation line L5 is a line branching from the first supply line L1 downstream of the compressor 120 and connected to the first supply line L1 upstream of the compressor 120.
  • a sixth valve 196 may be installed to control the flow rate and opening / closing of the boil-off gas.
  • the present embodiment in which the refrigerant cycle is configured as an open loop is, in comparison with the first and second embodiments in which the refrigerant cycle is configured as a closed loop, in that the downstream line of the compressor 120 and the downstream line of the spare compressor 122 are connected.
  • the second supply line (L2) downstream of the extra compressor 122 is connected to the first supply line (L1) downstream of the compressor 120, the evaporated gas compressed by the extra compressor 122 Is combined with the compressed boil-off gas by the compressor 120 and then sent to the refrigerant heat-exchanger 140, the fuel demand 180, or the boil-off gas heat exchanger 110.
  • This embodiment includes all other variants in which the downstream line of the compressor 120 and the downstream line of the spare compressor 122 are connected.
  • the demand amount in the fuel demand unit 180 increases, such as an increase in the operating speed of the ship, it is compressed by the spare compressor 122 as well as the boil-off gas compressed by the compressor 120.
  • the evaporated gas can also be sent to the fuel demand (180).
  • the compressor 120 and the spare compressor 122 are designed to have a capacity of approximately 1.2 times the amount required by the fuel demand 180, so that the excess compressor 122 exceeds the capacity of the compressor 120.
  • the boil-off gas compressed by is also required to be sent to the fuel demand unit 180, it hardly occurs. Rather, it is not possible to consume all of the evaporated gas discharged from the storage tank T in the fuel demand unit 180, and the amount of the evaporated gas to be reliquefied increases. More frequent
  • the boil-off gas compressed by the compressor 120 can be used as a refrigerant for heat exchange in the refrigerant heat exchanger 140.
  • the evaporated gas supplied to the refrigerant heat exchanger 140 along the return line (L3) can be cooled to a lower temperature using more refrigerant, and the overall reliquefaction efficiency and reliquefaction Volume can be increased, and theoretically 100% reliquefaction is also possible.
  • the compressor 120, the cooler 130, the spare compressor 122, and the spare cooler 132 are all operated, and the compressor 120 or the cooler 130 fails, the reliquefaction efficiency and reliquefaction are also opened. Abandoning the amount, the first valve 191 and the second valve 192 are closed to operate the system only with the boil-off gas passed through the spare compressor 122 and the extra cooler 132.
  • the compressor 120 and the cooler 130 plays a main role
  • the spare compressor 122 and the spare cooler 132 play a secondary role
  • the compressor 120 and the spare compressor ( 122), the cooler 130 and the extra cooler 132 have the same role and are provided with two or more compressors and coolers having the same role in one ship, so that in case one fails, it can be replaced with other equipment. In that sense, it satisfies the concept of redundancy. The same applies to the following.
  • the amount of the boil-off gas to be reliquefied is very small. With or without. Therefore, when the vessel is operating at high speed, only one of the compressor 120 or the spare compressor 122 may be driven.
  • the compressor 120 and the spare compressor 122 may compress the boil-off gas to the pressure required by the fuel demand 180, the fuel demand 180 may be an engine, a generator, or the like driven by the fuel.
  • the compressor 120 and the spare compressor 122 may compress the boil-off gas to a pressure of approximately 10 to 100 bar.
  • the compressor 120 and the extra compressor 122 may compress the boil-off gas to a pressure of approximately 150 bar to 400 bar when the fuel demand 180 is a ME-GI engine, and the fuel demand 180 is DFDE.
  • the boil-off gas may be compressed to a pressure of approximately 6.5 bar, and when the fuel demand unit 180 is an X-DF engine, the boil-off gas may be compressed to a pressure of approximately 16 bar.
  • the fuel demand unit 180 may include various types of engines.
  • the compressor 120 and the spare compressor 122 may include an X-DF engine. It is possible to compress the boil-off gas to the required pressure and install a decompression device upstream of the DFDE to lower the part of the boil-off boiled gas up to the pressure required by the X-DF engine to the pressure required by the DFDE before supplying it to the DFDE. .
  • the pressure of the boil-off gas is reduced by the compressor 120 or the spare compressor 122. Compresses the boil-off gas so as to exceed the pressure required by the 180, and installs a decompression device upstream of the fuel demand 180, the pressure of the boil-off gas compressed to exceed the pressure required by the fuel demand 180, the fuel demand After the pressure is lowered to 180, the fuel may be supplied to the fuel demand 180.
  • the compressor 120 and the spare compressor 122 may each be a multistage compressor.
  • one compressor 120 or 122 is used to compress the boil-off gas to the pressure required by the fuel demand 180, but when the compressor 120 and the spare compressor 122 are a multistage compressor, evaporation is performed.
  • the gas may be compressed several times by the plurality of compression cylinders up to the pressure required by the fuel demand 180.
  • a plurality of compression cylinders may be installed in series in the compressor 120 and the spare compressor 122, and a plurality of coolers may be disposed downstream of the plurality of compression cylinders. Each can be installed.
  • the cooler 130 of the present embodiment is installed downstream of the compressor 120 to cool the evaporated gas compressed by the compressor 120 and rises not only in pressure but also in temperature, and the spare cooler 132 of the present embodiment has a spare compressor. (122) It is provided downstream to cool the boil-off gas which is compressed by the extra compressor 122 to raise not only the pressure but also the temperature.
  • the cooler 130 and the extra cooler 132 may cool the boil-off gas through heat exchange with seawater, fresh water or air introduced from the outside.
  • the refrigerant heat exchanger 140 of the present embodiment further cools the boil-off gas supplied to the refrigerant heat exchanger 140 along the return line L3 after being cooled by the boil-off gas heat exchanger 110 and the refrigerant of the present embodiment.
  • the pressure reducing device 160 expands the boil-off gas passing through the refrigerant heat exchanger 140 and sends the same to the refrigerant heat exchanger 140 again.
  • the refrigerant heat exchanger 140 expands the evaporated gas supplied to the refrigerant heat exchanger 140 along the return line L3 after passing through the evaporation gas heat exchanger 110 by the refrigerant pressure reducing device 160.
  • the evaporated gas is heat-exchanged with a refrigerant and further cooled.
  • the refrigerant pressure reducing device 160 of the present embodiment may be various means for lowering the pressure of the fluid, and the state of the fluid immediately before passing through the refrigerant pressure reducing device 160 and the state of the fluid immediately after the passage are dependent on the operating conditions of the system. It may vary. However, when the refrigerant pressure reducing device 160 is an expander, in order to prevent physical damage of the refrigerant pressure reducing device 160, the fluid immediately before passing through the refrigerant pressure reducing device 160 and the fluid immediately after passing are maintained in the gas phase. It is preferable to be. The same applies to the following.
  • the boil-off gas used as the refrigerant for heat exchange in the refrigerant heat exchanger 140 may include boil-off gas compressed by the compressor 120 and boil-off gas compressed by the extra compressor 122.
  • a part of the combined evaporated gas is supplied to the refrigerant heat exchanger 140 along the recirculation line L5 to heat exchange the evaporated gas passed through the refrigerant pressure reducing device 160 in the refrigerant heat exchanger 140 with the refrigerant.
  • the refrigerant is supplied to the pressure reducing device 160.
  • the boil-off gas supplied from the first supply line (L1) to the refrigerant heat exchanger 140 along the recycle line (L5) is first cooled in the refrigerant heat exchanger (140) and further added by the refrigerant pressure reducing device (160). After cooling, it is sent to the refrigerant heat exchanger 140 to be used as a refrigerant.
  • the flow of the boil-off gas compressed by the compressor 120 is combined with the boil-off gas compressed by the extra compressor 122 and then supplied to the refrigerant heat exchanger 140 along the recirculation line L5.
  • the evaporated gas supplied to the refrigerant heat exchanger 140 along the return line (L3); both are heat exchanged by using the evaporated gas passed through the refrigerant pressure reducing device 160 as a refrigerant Is cooled.
  • the first pressure reducing device 150 of the present embodiment is installed on the return line L3 to expand the boil-off gas cooled by the boil-off gas heat exchanger 110 and the coolant heat exchanger 140.
  • the boil-off gas compressed by the compressor 120 joins the boil-off gas compressed by the spare compressor 122, and then partially branches, and the boil-off gas heat exchanger 110 and the refrigerant heat exchanger along the return line L3. 140 and the first decompression device 150 are partially or all reliquefied.
  • the first pressure reducing device 150 includes all means capable of expanding and cooling the boil-off gas and may be an expansion valve such as a Joule-Thomson valve or an expander.
  • the gas-liquid separator 170 is installed on the return line (L3) downstream of the first decompression device 150 and separates the gas-liquid mixture discharged from the first decompression device 150 into a gas and a liquid. It may include.
  • the liquid or gaseous gas in the gas-liquid mixed state passing through the first decompression device 150 is directly sent to the storage tank (T).
  • the boil-off gas passing through the first decompression device 150 is sent to the gas-liquid separator 170 to separate the gas phase and the liquid phase.
  • the liquid separated by the gas-liquid separator 170 is returned to the storage tank T along the return line L3, and the gas separated by the gas-liquid separator 170 is separated from the gas-liquid separator 170 by the evaporative gas heat exchanger ( 110 is supplied to the boil-off gas heat exchanger 110 along the gas discharge line L4 extending upstream of the first supply line L1.
  • the vessel of the present embodiment includes a gas-liquid separator 170
  • the seventh valve (197) for controlling the flow rate of the liquid separated by the gas-liquid separator 170 and sent to the storage tank (T);
  • an eighth valve 198 that controls the flow rate of the gas separated by the gas-liquid separator 170 and sent to the boil-off gas heat exchanger 110.
  • the first to eighth valves and the eleventh valves of the present exemplary embodiment 191, 192, 193, 194, 195, 196, 197, 198, and 203 may be manually adjusted by a person directly determining a system operating situation. It may be automatically adjusted to open and close by a preset value.
  • the main flow of the boil-off gas is defined to easily explain the operation of the apparatus for boil-off gas reliquefaction according to an embodiment of the present invention.
  • the evaporation gas generated in the storage tank T and the gas discharged from the gas-liquid separator 170 are supplied to the evaporative gas heat exchanger 110 in the first flow 100 and the evaporative gas heat exchanger 110 in the compressor ( 120 is supplied to the spare compressor 122 and then discharged from the compressor 120 or the spare compressor 122 and supplied to the fuel demand 180, the second flow 102, the compressor 120 and the spare compressor ( 122) flow downstream from the second stream 102 and supplied to the refrigerant heat exchanger 140 from the second stream 102 downstream from the third stream 104, the compressor 120 and the spare compressor 122;
  • the flow branched to the boil-off gas heat exchanger 110 is defined as the fourth flow 106 and the flow supplied to the refrigerant heat exchanger 140 from the boil-off gas heat exchanger 110 as the fifth flow 108.
  • the first flow 100 passes through
  • the gaseous boil-off gas generated in the storage tank T storing the liquid liquefied gas is supplied to the boil-off gas heat exchanger 110.
  • the gaseous evaporated gas generated in the storage tank (T) meets the gaseous evaporated gas discharged from the gas-liquid separator 170 after a predetermined time after the system operation to form the first flow (100). do.
  • the boil-off gas supplied to the boil-off gas heat exchanger 110 is the first flow 100.
  • the boil-off gas heat exchanger 110 recovers the cold heat of the first flow 100 to cool other boil-off gas. That is, the boil-off gas heat exchanger 110 recovers the cold heat of the first flow 100 and is supplied back to the boil-off gas heat exchanger 110 in the second flow 102, that is, the fourth flow. The recovered cold heat is transferred to 106.
  • boil-off gas heat exchanger 110 heat exchange occurs between the first flow 100 and the fourth flow 106, so that the first flow 100 is heated and the fourth flow 106 is cooled.
  • the heated first flow 100 becomes the second flow 102 and the cooled fourth flow 106 becomes the fifth flow 108.
  • the second stream 102 discharged from the boil-off gas heat exchanger 110 is supplied to the compressor 120 or the spare compressor 122, and compressed by the compressor 120 or the spare compressor 122.
  • the second stream 102 in which the boil-off gas compressed by the compressor 120 and the boil-off gas compressed in the spare compressor 122, is combined, is part of the third flow 104 as a refrigerant in the refrigerant heat exchanger 140.
  • the other part is supplied to the boil-off gas heat exchanger 110 as a fourth flow 106 and cooled, and the other part is supplied to the fuel demand 180.
  • the third flow 104 supplied to the refrigerant heat exchanger 140 is discharged from the refrigerant heat exchanger 140, expanded in the refrigerant pressure reducing device 160, and then supplied to the refrigerant heat exchanger 140 again.
  • the third flow 104 which is primarily supplied to the refrigerant heat exchanger 140, is expanded by the refrigerant pressure reducing device 160, and then the third flow 104 is supplied to the refrigerant heat exchanger 140 again.
  • the third stream 104 which has passed through the refrigerant pressure reducing device 160 and the refrigerant heat exchanger 140, joins the second stream 102 discharged from the boil-off gas heat exchanger 110, thereby providing a compressor 120 or a spare. It is supplied to the compressor 122.
  • the fifth flow 108 supplied to the refrigerant heat exchanger 140 is cooled by heat exchange with the third flow 104 passing through the refrigerant pressure reducing device 160, and then expands while passing through the first pressure reducing device 150. do.
  • the fifth flow 108 through the first pressure reducing device 150 is in a gas-liquid mixture, in which gas and liquid are mixed.
  • the fifth stream 108 in the gas-liquid mixture is directly sent to the storage tank T or separated into gas and liquid while passing through the gas-liquid separator 170.
  • the liquid separated by the gas-liquid separator 170 is supplied to the storage tank T, and the gas separated by the gas-liquid separator 170 is supplied to the boil-off gas heat exchanger 110 to repeat the above processes.
  • FIG. 5 is a configuration diagram schematically showing a boil-off gas treatment system according to a fourth embodiment of the present invention.
  • the ship of the fourth embodiment shown in FIG. 5 further includes a ninth valve 201, a tenth valve 202 and a first additional line L6 as compared to the ship of the third embodiment shown in FIG. 4.
  • the refrigerant cycle may be operated as a closed loop as in the first and second embodiments, and the refrigerant cycle may be operated as an open loop as in the third embodiment. Differences exist in that they will be described below. Detailed descriptions of the same members as those of the ship of the third embodiment are omitted.
  • the vessel of the present embodiment like the third embodiment, has a boil-off gas heat exchanger 110, a first valve 191, a compressor 120, a cooler 130, and a second valve 192.
  • the storage tank T of the present embodiment stores the liquefied gas such as liquefied natural gas and liquefied ethane gas inside, and discharges the boil-off gas to the outside when the internal pressure is higher than the predetermined pressure.
  • the boil-off gas discharged from the storage tank T is sent to the boil-off gas heat exchanger 110.
  • the boil-off gas heat exchanger 110 of the present embodiment uses the boil-off gas discharged from the storage tank T as a refrigerant and goes to the boil-off gas heat exchanger 110 along the return line L3. Cool the sent boil-off gas. That is, the boil-off gas heat exchanger 110 recovers the cold heat of the boil-off gas discharged from the storage tank T and transfers the collected cold heat to the boil-off gas sent to the boil-off gas heat exchanger 110 along the return line L3.
  • a fifth valve 195 may be installed on the return line L3 to control the flow rate and opening and closing of the boil-off gas.
  • the compressor 120 of the present embodiment is installed on the first supply line L1 to compress the evaporated gas discharged from the storage tank T, and the extra compressor 122 of the present embodiment , Like the third embodiment, is installed in parallel with the compressor 120 on the second supply line (L2) to compress the boil-off gas discharged from the storage tank (T).
  • Compressor 120 and spare compressor 122 may be a compressor of the same performance, each may be a multi-stage compressor.
  • the compressor 120 and the spare compressor 122 of this embodiment can compress the boil-off gas to the pressure required by the fuel demand 180 as in the third embodiment.
  • some of the high pressures are compressed after compressing the boil-off gas in accordance with a required pressure of an engine requiring higher pressure (hereinafter, referred to as a 'high pressure engine'). It can be supplied to the engine, and the other part can be supplied to the low pressure engine after being depressurized by a pressure reducing device installed upstream of the engine requiring a lower pressure (hereinafter referred to as a 'low pressure engine').
  • the boil-off gas is supplied to the fuel demand unit 180 by the compressor 120 or the spare compressor 122. Pressure to a pressure higher than the pressure required, and a pressure reducing device is installed upstream of the fuel demand unit 180 to lower the pressure of the boil-off gas compressed to high pressure to the pressure required by the fuel demand unit 180, and then to the fuel demand unit 180. You can also supply.
  • the vessel of this embodiment further includes an eleventh valve 203 which is provided upstream of the fuel demand unit 180 and regulates the flow rate and opening and closing of the boil-off gas sent to the fuel demand unit 180. Can be.
  • the vessel of this embodiment uses the evaporated gas compressed by the extra compressor 122 as a refrigerant for additionally cooling the evaporated gas in the refrigerant heat exchanger 140, so that the reliquefaction efficiency and reliquefaction amount Can increase.
  • the cooler 130 of the present embodiment is installed downstream of the compressor 120 to cool the evaporated gas passing through the compressor 120 and the temperature as well as the pressure
  • the extra cooler of the present embodiment 132, like the third embodiment, is installed downstream of the extra compressor 122 to cool the evaporated gas that has passed through the extra compressor 122 and has risen in temperature as well as pressure.
  • Refrigerant heat exchanger 140 of the present embodiment is supplied to the boil-off gas heat exchanger 110 along the return line (L3), and the boil-off gas cooled by the boil-off gas heat exchanger (110) Cool additionally.
  • the evaporated gas discharged from the storage tank T is further cooled not only in the evaporation gas heat exchanger 110 but also in the refrigerant heat exchanger 140, so that the temperature is lower. Since it can be supplied to the first decompression device 150, the reliquefaction efficiency and the amount of reliquefaction are increased.
  • the refrigerant pressure reducing device 160 expands the evaporated gas passing through the refrigerant heat exchanger 140 and sends it to the refrigerant heat exchanger 140 in the same manner as in the third embodiment.
  • the first pressure reducing device 150 of the present embodiment is installed on the return line L3 to supply the boil-off gas cooled by the boil-off gas heat exchanger 110 and the refrigerant heat exchanger 140. Inflate.
  • the first pressure reducing device 150 of the present embodiment includes all means capable of expanding and cooling the boil-off gas, and may be an expansion valve such as a Joule-Thomson valve or an expander.
  • the vessel of the present embodiment is installed on the return line L3 downstream of the first pressure reducing device 150 and separates the gas-liquid mixture discharged from the first pressure reducing device 150 into gas and liquid.
  • Gas-liquid separator 170 may be included.
  • the vessel of this embodiment does not include the gas-liquid separator 170
  • the liquid or gaseous-mixed evaporated gas that has passed through the first decompression device 150 is directly sent to the storage tank T.
  • the vessel of the present embodiment includes the gas-liquid separator 170
  • the boil-off gas passing through the first pressure reducing device 150 is sent to the gas-liquid separator 170 to separate the gas phase and the liquid phase.
  • the liquid separated by the gas-liquid separator 170 is returned to the storage tank T along the return line L3, and the gas separated by the gas-liquid separator 170 is separated from the gas-liquid separator 170 by the evaporative gas heat exchanger ( 110 is supplied to the boil-off gas heat exchanger 110 along the gas discharge line L4 extending upstream of the first supply line L1.
  • the vessel of the present embodiment includes the gas-liquid separator 170, like the third embodiment, the seventh valve (197) for controlling the flow rate of the liquid separated by the gas-liquid separator 170 and sent to the storage tank (T) ); And an eighth valve 198 that controls the flow rate of the gas separated by the gas-liquid separator 170 and sent to the boil-off gas heat exchanger 110.
  • the ship of this embodiment unlike the third embodiment, the first additional line (L6) for connecting between the recirculation line (L5) and the second supply line (L2); A ninth valve 201 installed on the recirculation line L5; And a tenth valve 202 installed on the first additional line L6.
  • the ship of the present embodiment unlike the third embodiment, which selectively includes the sixth valve, the recirculation line (L5) through which the boil-off gas branched from the first supply line (L1) is sent to the refrigerant heat exchanger (140). And a sixth valve 196 that controls the flow rate and opening and closing of the boil-off gas.
  • One side of the first additional line (L6) of the present embodiment after the expansion by the refrigerant pressure reducing device 160, and sends the evaporated gas passed through the refrigerant heat exchanger 140 to the first supply line (L1), recirculation line ( It is connected on the L5, the other side is connected on the second supply line (L2) between the third valve (193) and the spare compressor (122).
  • the ninth valve 201 of the present embodiment has a point where the recirculation line L5 meets the first supply line L1 upstream of the compressor 120 and the spare compressor 122, and the recirculation line L5 is first added. Between the point where it meets the line L6, it is installed on the recirculation line L5.
  • the ship of the present embodiment the second compressor line (L2) downstream of the extra compressor 122 is connected to the recirculation line (L5) rather than the first supply line (L1).
  • the first to eleventh valves 191, 192, 193, 194, 195, 196, 197, 198, 201, 202, and 203 of the present embodiment may be manually adjusted by a person directly determining a system operating situation. It may be automatically adjusted to open and close by a preset value.
  • a feature that is different from the third embodiment of the ship of this embodiment is that the refrigerant cycle can be operated not only in the open loop but also in the closed loop, so that the reliquefaction system can be used more flexibly according to the operating conditions of the ship.
  • the method of operating the refrigerant cycle in the closed loop and the method of operating in the open loop through the valve adjustment will be described.
  • the third valve 193 is closed to supply the boil-off gas to the extra compressor 122 and the extra cooler.
  • the fourth valve 194 the refrigerant heat exchanger 140, the refrigerant pressure reducing device 160, the refrigerant heat exchanger 140, and the tenth valve 202.
  • the storage tank including the storage tank of the present embodiment may further include a pipe for introducing nitrogen gas into the refrigerant cycle of the closed loop.
  • the refrigerant cycle When the refrigerant cycle is operated as a closed loop, only the boil-off gas circulating in the closed loop is used as the refrigerant in the refrigerant heat exchanger 140, and the boil-off gas passing through the compressor 120 is not introduced into the refrigerant cycle and the fuel demand ( 180 or the reliquefaction process is performed along the return line (L3). Therefore, regardless of the amount of reliquefaction and the amount of boil-off gas required by the fuel demand unit 180, the boil-off gas of a constant flow rate is circulated to the refrigerant of the refrigerant heat exchanger 140.
  • the evaporated gas discharged from the storage tank (T) passes through the boil-off gas heat exchanger (110) and is compressed by the compressor (120) and cooled by the cooler (130), a part is sent to the fuel demand (180), The other part is sent to the boil-off gas heat exchanger 110 along the return line (L3).
  • the boil-off gas sent to the boil-off gas heat exchanger 110 along the return line L3 is heat-exchanged with the boil-off gas discharged from the storage tank T and then cooled, and further cooled by heat-exchange in the refrigerant heat exchanger 140.
  • the boil-off gas cooled by the boil-off gas heat exchanger 110 and the refrigerant heat exchanger 140 is expanded by the first pressure reducing device 150 to re-liquefy some or all of the boil-off gas.
  • some or all of the re-liquefied boil-off gas is sent directly to the storage tank (T), when the vessel of this embodiment includes the gas-liquid separator 170 Partially or wholly reliquefied boil-off gas is sent to the gas-liquid separator 170.
  • the gas separated by the gas-liquid separator 170 is combined with the boil-off gas discharged from the storage tank T and sent to the boil-off gas heat exchanger 110, and the liquid separated by the gas-liquid separator 170 is stored in the storage tank ( Sent to T).
  • the boil-off gas circulating through the refrigerant cycle is compressed by the extra compressor 122 and cooled by the extra cooler 132 and then sent to the refrigerant heat exchanger 140 along the recirculation line L5.
  • the evaporated gas sent to the refrigerant heat exchanger 140 is first heat-exchanged by the refrigerant heat exchanger 140, cooled, and then sent to the refrigerant pressure reducing device 160. Inflated and cooled by car.
  • the evaporated gas passing through the refrigerant pressure reducing device 160 is sent to the refrigerant heat exchanger 140 again, and passes through the evaporative gas heat exchanger 110, and then evaporates supplied to the refrigerant heat exchanger 140 along the return line L3. gas; And a boil-off gas compressed by the extra compressor 122 and supplied to the refrigerant heat exchanger 140 along the recirculation line L5. After passing through the refrigerant pressure reducing device 160, the boil-off gas used as the refrigerant in the refrigerant heat exchanger 140 is sent to the spare compressor 122 again and repeats the above-described series of processes.
  • the first valve 191, the second valve 192, and the tenth valve 202 may be The third valve 193 and the sixth valve 196 are opened, and the boil-off gas passed through the boil-off gas heat exchanger 110 after being discharged from the storage tank T is connected to the third valve 193 and the spare compressor.
  • the fuel is supplied to the fuel demand 180 through the 122, the extra cooler 132, the fourth valve 194, and the sixth valve 196.
  • the ninth valve 201 may be opened to operate the system.
  • the first valve 191, the second valve 192, the third valve 193, the fourth valve 194, the sixth valve 196 and The ninth valve 201 is opened and the tenth valve 202 is closed.
  • the boil-off gas circulating through the refrigerant cycle and the boil-off gas sent to the fuel demand 180 or undergoing reliquefaction along the return line L3 are separated.
  • the refrigerant cycle is operated as an open loop, the boil-off gas compressed by the compressor 120 and the boil-off gas compressed by the extra compressor 122 are combined to be used as a refrigerant in the refrigerant heat exchanger 140 or to be fueled. It is sent to the customer 180, or undergoes a reliquefaction process along the return line (L3).
  • the flow rate of the refrigerant sent to the refrigerant heat exchanger 140 may be flexibly adjusted in consideration of the amount of reliquefaction and the amount of boil-off gas at the fuel demand 180.
  • the amount of boil-off gas in the fuel demand unit 180 is small, increasing the flow rate of the refrigerant sent to the refrigerant heat exchanger 140 may increase the reliquefaction efficiency and the amount of reliquefaction.
  • the boil-off gas discharged from the storage tank T passes through the boil-off gas heat exchanger 110 and then branches into two streams, partly to the first supply line L1, and the other part to the second supply line L2. Is sent to.
  • the boil-off gas sent to the first supply line L1 passes through the first valve 191, the compressor 120, the cooler 130, and the second valve 192, and then a part thereof passes through the sixth valve 196. It is sent to the refrigerant heat exchanger 140, and the other part again branches into two flows. One stream of the boil-off gas branched into two streams is sent to the fuel demand unit 180, and the other is sent to the boil-off gas heat exchanger 110 along the return line (L3).
  • the boil-off gas sent to the second supply line L2 passes through the third valve 193, the spare compressor 122, the extra cooler 132, and the fourth valve 194, and a part thereof is a refrigerant heat exchanger 140. ), The other part is sent to the first supply line (L1) and branches into two flows. One stream of the boil-off gas branched into two streams is sent to the fuel demand unit 180, and the other stream is sent to the boil-off gas heat exchanger 110 along the return line L3.
  • the evaporated gas compressed by the compressor 120 and the evaporated gas compressed by the extra compressor 122 have been described separately, but the evaporated gas and the extra compressor 122 compressed by the compressor 120 are described.
  • the compressed boil-off gas is not separately flowed, but rather joined and supplied to the refrigerant heat exchanger 140, the fuel demand 180, or the boil-off gas heat exchanger 110.
  • the line L3 the boil-off gas compressed by the compressor 120 and the boil-off gas compressed by the extra compressor 122 are mixed and flow.
  • the evaporated gas sent to the refrigerant heat exchanger 140 along the recirculation line L5 is first heat exchanged and cooled in the refrigerant heat exchanger 140, and is secondly expanded and cooled by the refrigerant pressure reducing device 160, and then again the refrigerant.
  • the heat exchanger 140 is supplied. After passing through the refrigerant pressure reducing device 160, the boil-off gas supplied to the refrigerant heat exchanger 140 passes through the boil-off gas heat exchanger 110 and then is supplied to the refrigerant heat exchanger 140 along the return line L3.
  • the boil-off gas used as the refrigerant in the refrigerant heat exchanger 140 is supplied to the refrigerant heat exchanger 140 along the recirculation line L5, and then is first cooled in the refrigerant heat exchanger 140, and the refrigerant pressure reducing device ( It is the boil-off gas cooled by secondary by 160.
  • the boil-off gas sent from the compressor 120 or the spare compressor 122 to the refrigerant heat exchanger 140 along the recirculation line L5 cools the boil-off gas passed through the refrigerant pressure reducing device 160 as a refrigerant. .
  • the boil-off gas used as the refrigerant in the refrigerant heat exchanger 140 is sent to the first supply line L1 through the ninth valve 201 and discharged from the storage tank T. After the evaporated gas heat exchanger 110 is joined with the evaporated gas, the above-described series of processes are repeated.
  • the boil-off gas sent to the boil-off gas heat exchanger 110 along the return line L3 is first cooled in the boil-off gas heat exchanger 110 and secondly cooled in the refrigerant heat exchanger 140, followed by a first pressure reducing device ( 150) to re-liquefy some or all of it.
  • the vessel of this embodiment does not include the gas-liquid separator 170, some or all of the re-liquefied boil-off gas is sent directly to the storage tank (T), when the vessel of this embodiment includes the gas-liquid separator 170 Partially or wholly reliquefied boil-off gas is sent to the gas-liquid separator 170.
  • the gas separated by the gas-liquid separator 170 is combined with the boil-off gas discharged from the storage tank T and sent to the boil-off gas heat exchanger 110, and the liquid separated by the gas-liquid separator 170 is stored in the storage tank ( Sent to T).
  • the first valve 191, the second valve 192, and the ninth valve 201 are replaced. Closed, the boil-off gas discharged from the storage tank T and passed through the boil-off gas heat exchanger 110, the third valve 193, the spare compressor 122, the extra cooler 132, the fourth valve 194 And a sixth valve 196 to be supplied to the fuel demand 180.
  • the ninth valve 201 may be opened to operate the system.
  • the liquefied gas stored in the storage tank (T) is liquefied natural gas
  • the fuel demand 180 is an X-DF engine
  • a gas-liquid separator (170) For example, the temperature and pressure of the fluid at each point are described as follows.
  • the boil-off gas discharged from the storage tank T and the boil-off gas separated by the gas-liquid separator 170 are combined to be supplied to the boil-off gas heat exchanger 110, and the boil-off gas at the point A is approximately -120 ° C and 1.060 bara.
  • the boil-off gas at point B after the boil-off gas of approximately -120 ° C. and 1.060 bara is heat-exchanged in the boil-off gas heat exchanger 110 with the boil-off gas of about 43 ° C. and 20 bara is approximately 3 ° C., 0.96 may be bara.
  • the boil-off gas having a temperature of approximately 3 ° C. and 0.96 bara has joined the boil-off gas having approximately 20 ° C. and 0.96 bara passing through the refrigerant heat exchanger 140 after passing through the refrigerant pressure reducing device 160.
  • the boil-off gas may be 0.96 bara at approximately 15 ° C.
  • the boil-off gas approximately 15 ° C., 0.96 bara, is branched into two, one stream is compressed by the compressor 120 and then cooled by the cooler 130, and the other stream is compressed by the spare compressor 122 and then the extra cooler. Cooled by 132, the evaporation gas at point D, which is the flow of the flow through the compressor 120 and the cooler 130 and the flow through the spare compressor 122 and the extra cooler 132 are combined.
  • the boil-off gas at point H may be approximately 43 ° C., 20 bara.
  • the boil-off gas at point E after the boil-off gas of approximately 43 ° C. and 20 bara is heat-exchanged in the boil-off gas heat exchanger 110 with the boil-off gas of approximately ⁇ 120 ° C. and 1.060 bara may be approximately ⁇ 110 ° C. and 20 bara.
  • the evaporation gas at point F may be about ⁇ 153 ° C. and 20 bara.
  • the boil-off gas at point G after being expanded by the first pressure reducing device 150 may be ⁇ 157 ° C. and 2.1 bara.
  • the boil-off gas at point I after the boil-off gas having approximately 43 ° C. and 20 bara is first cooled by the refrigerant heat exchanger 140 may be about ⁇ 73 ° C. and 20 bara, and the evaporation of about ⁇ 73 ° C. and 20 bara.
  • the boil-off gas at point J after the gas is secondarily cooled by the refrigerant pressure reducing device 160 may be approximately -154 ° C and 1.56 bara, and the boil-off gas at approximately -154 ° C and 1.56 bara is the refrigerant heat exchanger 140.
  • the evaporated gas at point K, after being used as a refrigerant in), may be approximately 20 ° C. and 0.96 bara.
  • the vessel of the present embodiment operates the refrigerant cycle in an open loop
  • the evaporated gas compressed by the extra compressor 122 is used only as the refrigerant of the refrigerant heat exchanger 140
  • the evaporated gas compressed by the compressor 120 is
  • the spare compressor 122 and the compressor 120 are independently provided so as to be sent to the fuel demand 180 or to undergo a reliquefaction process along the return line L3 and not to be used as the refrigerant of the refrigerant heat exchanger 140. It can also be operated.
  • the refrigerant cycle of the open loop for independently operating the spare compressor 122 and the compressor 120 is referred to as an 'independent open loop'.
  • the refrigerant cycle is operated in an independent open loop, there is an advantage in that the operation of the system is easier than in the open loop.
  • the boil-off gas discharged from the storage tank T passes through the boil-off gas heat exchanger 110 and then branches into two streams, partly to the first supply line L1, and partly to the second supply line L2. Is sent.
  • the boil-off gas sent to the first supply line L1 passes through the first valve 191, the compressor 120, the cooler 130, and the second valve 192, and a part of the boil-off gas is sent to the fuel demand 180. , The other part is sent to the boil-off gas heat exchanger 110 along the return line (L3).
  • the boil-off gas sent to the second supply line L2 passes through the third valve 193, the spare compressor 122, the extra cooler 132, and the fourth valve 194, and then cools the refrigerant along the recycle line L5. Sent to heat exchanger 140.
  • the boil-off gas which is compressed by the extra compressor 122 and sent to the refrigerant heat exchanger 140 along the recirculation line L5, is first heat-exchanged by the refrigerant heat exchanger 140 and cooled, and is then cooled to the refrigerant pressure reducing device 160. After the second expansion by the cooling to be supplied to the refrigerant heat exchanger 140 again, passing through the boil-off gas heat exchanger 110, the boil-off gas supplied to the refrigerant heat exchanger 140 through the return line (L3); And a boil-off gas compressed by the extra compressor 122 and supplied to the refrigerant heat exchanger 140 along the recirculation line L5.
  • the boil-off gas used as the refrigerant in the refrigerant heat exchanger 140 is sent to the first supply line L1 through the ninth valve 201 and discharged from the storage tank T. After the evaporated gas heat exchanger 110 is joined with the evaporated gas, the above-described process is repeated.
  • the boil-off gas which is compressed by the compressor 120 and then sent to the boil-off gas heat exchanger 110 along the return line L3, is first cooled in the boil-off gas heat exchanger 110, and then cooled in the refrigerant heat exchanger 140. After cooling by the car, the first pressure reducing device 150 is expanded to re-liquefy a part or all of the liquid.
  • the vessel of this embodiment does not include the gas-liquid separator 170, some or all of the re-liquefied boil-off gas is sent directly to the storage tank (T), when the vessel of this embodiment includes the gas-liquid separator 170 Partially or wholly reliquefied boil-off gas is sent to the gas-liquid separator 170.
  • the gas separated by the gas-liquid separator 170 is combined with the boil-off gas discharged from the storage tank T and sent to the boil-off gas heat exchanger 110, and the liquid separated by the gas-liquid separator 170 is stored in the storage tank ( Sent to T).
  • the first valve 191, the second valve 192, and the ninth valve 201 are damaged. 6, the first valve 196 is opened, and the boil-off gas passed through the boil-off gas heat exchanger 110 after being discharged from the storage tank T is connected to the third valve 193, the spare compressor 122, and the extra cooler. 132, the fourth valve 194 and the sixth valve 196 are supplied to the fuel demand 180.
  • the ninth valve 201 may be opened to operate the system.
  • Figure 6 is a schematic diagram showing a system for treating the boil-off gas in accordance with a fifth embodiment of the present invention.
  • the ship of the fifth embodiment shown in FIG. 6 has a twelfth valve 301, a thirteenth valve 302, a fourteenth valve 303, and a fifteenth valve (compared with the ship of the fourth embodiment shown in FIG. 5). There is a difference in that 304, the second additional line L7, the third additional line L8, the fourth additional line L9, and the fifth additional line L10 are further added. Explain mainly. Detailed description of the same members as those of the ship of the fourth embodiment is omitted.
  • the vessel of the present embodiment like the fourth embodiment, has a boil-off gas heat exchanger 110, a first valve 191, a compressor 120, a cooler 130, and a second valve 192.
  • the storage tank T of the present embodiment stores the liquefied gas such as liquefied natural gas and liquefied ethane gas inside, and discharges the boil-off gas to the outside when the internal pressure is higher than the predetermined pressure.
  • the boil-off gas discharged from the storage tank T is sent to the boil-off gas heat exchanger 110.
  • the boil-off gas heat exchanger 110 uses the boil-off gas discharged from the storage tank T as a refrigerant to the boil-off gas heat exchanger 110 along the return line L3. Cool the sent boil-off gas.
  • the compressor 120 of the present embodiment is installed on the first supply line L1 to compress the evaporated gas discharged from the storage tank T, and the extra compressor 122 of the present embodiment , Like the fourth embodiment, is installed in parallel with the compressor 120 on the second supply line (L2) to compress the boil-off gas discharged from the storage tank (T).
  • Compressor 120 and spare compressor 122 may be a compressor of the same performance, each may be a multi-stage compressor.
  • the compressor 120 and the spare compressor 122 of this embodiment can compress the boil-off gas to the pressure required by the fuel demand 180 as in the fourth embodiment.
  • the fuel demand unit 180 includes several types of engines, after compressing the boil-off gas in accordance with the required pressure of the high pressure engine, part of the fuel supply unit 180 is supplied to the high pressure engine, and the other part is a pressure reducing device installed upstream of the low pressure engine Can be supplied to a low pressure engine.
  • the fuel demand 180 is supplied to the boil-off gas by the compressor 120 or the spare compressor 122.
  • a pressure reducing device is installed upstream of the fuel demand unit 180 to lower the pressure of the boil-off gas compressed to high pressure to the pressure required by the fuel demand unit 180, and then supply the fuel to the fuel unit unit 180. It may be.
  • the vessel of the present embodiment further includes an eleventh valve 203 which is provided upstream of the fuel demand unit 180 and controls the flow rate and opening and closing of the boil-off gas sent to the fuel demand unit 180. Can be.
  • the vessel of the present embodiment uses the evaporated gas compressed by the extra compressor 122 as a refrigerant for additionally cooling the evaporated gas in the refrigerant heat exchanger 140, so that the reliquefaction efficiency and the amount of reliquefaction are increased. Can increase.
  • the cooler 130 of the present embodiment is installed downstream of the compressor 120 to cool the evaporated gas that has passed through the compressor 120 and has risen in pressure as well as in temperature.
  • 132 is installed downstream of the extra compressor 122 to cool the evaporated gas that has passed through the extra compressor 122 and has risen in temperature as well as pressure.
  • Refrigerant heat exchanger 140 of the present embodiment is supplied to the boil-off gas heat exchanger 110 along the return line (L3), and the boil-off gas cooled by the boil-off gas heat exchanger (110) Cool additionally.
  • the evaporated gas discharged from the storage tank T is further cooled not only in the evaporation gas heat exchanger 110 but also in the refrigerant heat exchanger 140, so that the temperature is lowered. Since it can be supplied to the first decompression device 150, the reliquefaction efficiency and the amount of reliquefaction are increased.
  • the refrigerant pressure reducing device 160 expands the evaporated gas passing through the refrigerant heat exchanger 140 and sends it to the refrigerant heat exchanger 140 in the same manner as the fourth embodiment.
  • the first pressure reducing device 150 of the present embodiment is installed on the return line L3 to supply the boil-off gas cooled by the boil-off gas heat exchanger 110 and the refrigerant heat exchanger 140. Inflate.
  • the first pressure reducing device 150 of the present embodiment includes all means capable of expanding and cooling the boil-off gas, and may be an expansion valve such as a Joule-Thomson valve or an expander.
  • the vessel of this embodiment is installed on the return line L3 downstream of the first pressure reducing device 150 and separates the gas-liquid mixture discharged from the first pressure reducing device 150 into gas and liquid.
  • Gas-liquid separator 170 may be included.
  • the vessel of the present embodiment when the vessel of the present embodiment does not include the gas-liquid separator 170, the liquid or gaseous-mixed evaporated gas that has passed through the first pressure reducing device 150 is directly sent to the storage tank T.
  • the vessel of the present embodiment includes the gas-liquid separator 170, the boil-off gas passing through the first pressure reducing device 150 is sent to the gas-liquid separator 170 to separate the gas phase and the liquid phase.
  • the liquid separated by the gas-liquid separator 170 is returned to the storage tank T along the return line L3, and the gas separated by the gas-liquid separator 170 is separated from the gas-liquid separator 170 by the evaporative gas heat exchanger ( 110 is supplied to the boil-off gas heat exchanger 110 along the gas discharge line L4 extending upstream of the first supply line L1.
  • the vessel of the present embodiment includes the gas-liquid separator 170, like the fourth embodiment, the seventh valve (197) for controlling the flow rate of the liquid separated by the gas-liquid separator 170 and sent to the storage tank (T) ); And an eighth valve 198 that controls the flow rate of the gas separated by the gas-liquid separator 170 and sent to the boil-off gas heat exchanger 110.
  • the vessel of the present embodiment like the fourth embodiment, has a first additional line connecting the sixth valve 196, the recirculation line L5 and the second supply line L2 installed on the recirculation line L5. (L6); A ninth valve 201 installed on the recirculation line L5; And a tenth valve 202 installed on the first additional line L6.
  • first additional line L6 of the present embodiment similar to the fourth embodiment, one side of the first additional line L6 expands by the refrigerant pressure reducing device 160 and passes the evaporated gas passing through the refrigerant heat exchanger 140 in the first supply line ( It is connected to the recirculation line L5, which is sent to L1, and the other side is connected to the second supply line L2 between the third valve 193 and the spare compressor 122.
  • the second supply line L2 downstream of the redundant compressor 122 is connected to the first supply line L1 and the upstream of the refrigerant heat exchanger 140.
  • Recirculation line (L5) is connected to the second supply line (L2).
  • the ship of the present embodiment has a first additional line L6 upstream of the tenth valve 202 and a first supply line between the first valve 191 and the compressor 120.
  • Third additional line connecting the second supply line L2 between the extra cooler 132 and the fourth valve 194 and the first supply line L1 between the cooler 130 and the second valve 192.
  • a fourth additional line L9 connecting the first supply line L1 between the cooler 130 and the second valve 192 and the recirculation line L5 downstream of the sixth valve 196;
  • a fifth additional line L10 connecting the second supply line L2 between the extra cooler 132 and the fourth valve 194 and downstream of the fifth valve 195 of the return line L3.
  • the ship of this embodiment includes a fifth valve 195 installed on the return line L3; A twelfth valve 301 installed on the second additional line L7, a thirteenth valve 302 installed on the third additional line L8, and a fourteenth valve installed on the fourth additional line L9. 303, and a fifteenth valve 304 installed on the fifth additional line L10.
  • the first to fifteenth valves 191, 192, 193, 194, 195, 196, 197, 198, 201, 202, 203, 301, 302, 303, and 304 of the present embodiment directly determine a system operation situation. It may be adjusted manually or may be automatically adjusted to open and close by a preset value.
  • the refrigerant cycle of the ship of this embodiment can be operated as a closed loop, an open loop or an independent open loop.
  • the refrigerant cycle is closed loop, open loop or independent open loop. It explains how to operate.
  • the tenth valve 202 are opened, the fourth valve 194, the ninth valve 201, the twelfth valve 301, the thirteenth valve 302, the fourteenth valve 303, and the fifteenth valve. 304 drives the system in the closed state.
  • the third valve 193 is closed to supply the boil-off gas to the extra compressor 122 and the extra cooler.
  • the sixth valve 196, the refrigerant heat exchanger 140, the refrigerant pressure reducing device 160, the refrigerant heat exchanger 140, and the tenth valve 202 To form.
  • the nitrogen gas may be used as the refrigerant circulating in the closed loop, and may further include a pipe for introducing the nitrogen gas into the refrigerant cycle of the closed loop.
  • the evaporated gas discharged from the storage tank (T) passes through the boil-off gas heat exchanger (110) and is compressed by the compressor (120) and cooled by the cooler (130), a part is sent to the fuel demand (180), The other part is sent to the boil-off gas heat exchanger 110 along the return line (L3).
  • the boil-off gas sent to the boil-off gas heat exchanger 110 along the return line L3 is heat-exchanged with the boil-off gas discharged from the storage tank T and then cooled, and further cooled by heat-exchange in the refrigerant heat exchanger 140.
  • the boil-off gas cooled by the boil-off gas heat exchanger 110 and the refrigerant heat exchanger 140 is expanded by the first pressure reducing device 150 to re-liquefy some or all of the boil-off gas.
  • some or all of the re-liquefied boil-off gas is sent directly to the storage tank (T), when the vessel of this embodiment includes the gas-liquid separator 170 Partially or wholly reliquefied boil-off gas is sent to the gas-liquid separator 170.
  • the gas separated by the gas-liquid separator 170 is combined with the boil-off gas discharged from the storage tank T and sent to the boil-off gas heat exchanger 110, and the liquid separated by the gas-liquid separator 170 is stored in the storage tank ( Sent to T).
  • the boil-off gas circulating through the refrigerant cycle is compressed by the extra compressor 122 and cooled by the extra cooler 132 and then sent to the refrigerant heat exchanger 140 along the recirculation line L5.
  • the evaporated gas sent to the refrigerant heat exchanger 140 is first heat-exchanged by the refrigerant heat exchanger 140, cooled, and then sent to the refrigerant pressure reducing device 160. Inflated and cooled by car.
  • the evaporated gas passing through the refrigerant pressure reducing device 160 is sent to the refrigerant heat exchanger 140 again, and passes through the evaporative gas heat exchanger 110, and then evaporates supplied to the refrigerant heat exchanger 140 along the return line L3. gas; And a boil-off gas compressed by the extra compressor 122 and supplied to the refrigerant heat exchanger 140 along the recirculation line L5. After passing through the refrigerant pressure reducing device 160, the boil-off gas used as the refrigerant in the refrigerant heat exchanger 140 is sent to the spare compressor 122 again and repeats the above-described series of processes.
  • the first valve 191, the second valve 192, the fifth valve 195, The sixth valve 196 and the tenth valve 202 are closed, and the third valve 193 and the fourth valve 194 are opened to discharge the evaporative gas heat exchanger 110 after being discharged from the storage tank T.
  • the boil-off gas passed through the third valve 193, the spare compressor 122, the extra cooler 132, and the fourth valve 194 are supplied to the fuel demand 180.
  • the fifteenth valve 304 is opened to evaporate. Part of the gas may be subjected to the reliquefaction process along the return line (L3).
  • the sixth valve 196 and the ninth valve 201 may be opened, or sixth valve 196 and tenth valve 202 may be opened to operate the system.
  • the vessel of this embodiment uses the evaporated gas compressed by the compressor 120 as a refrigerant in the refrigerant heat exchanger 140 while the refrigerant cycle is operated as a closed loop, and uses the evaporated gas compressed by the spare compressor 122. It may be supplied to the fuel demand 180 or to undergo a reliquefaction process (hereinafter referred to as a 'second closed loop').
  • the compressor 120 and the cooler 130, the spare compressor 122 and the spare cooler 132 are merely described separately for convenience of description and play the same role, and play the same role in one ship. Redundancy concept is satisfied in that more than two compressors and coolers are provided. Therefore, the compressor 120, the cooler 130, the spare compressor 122, and the spare cooler 132 may be operated in different roles.
  • valve 302 drives the system in the closed state.
  • the first valve 191 When the boil-off gas compressed by the compressor 120 after being discharged from the storage tank T is supplied to the recirculation line L5, the first valve 191 is closed so that the boil-off gas is compressed by the compressor 120 and the cooler 130.
  • a closed loop refrigerant cycle is circulated through the fourteenth valve 303, the refrigerant heat exchanger 140, the refrigerant pressure reducing device 160, the refrigerant heat exchanger 140, and the twelfth valve 301.
  • the boil-off gas discharged from the storage tank T passes through the boil-off gas heat exchanger 110, passes through the third valve 193, is compressed by the spare compressor 122, and is cooled by the spare cooler 132. After that, a part is sent to the fuel demand 180 through the fourth valve 194 and the other part is sent to the boil-off gas heat exchanger 110 along the return line L3 through the fifteenth valve 304. .
  • the boil-off gas sent to the boil-off gas heat exchanger 110 is cooled by heat exchange with the boil-off gas discharged from the storage tank T, and then further cooled in the refrigerant heat exchanger 140.
  • the boil-off gas cooled by the boil-off gas heat exchanger 110 and the refrigerant heat exchanger 140 is expanded by the first pressure reducing device 150 to re-liquefy some or all of the boil-off gas.
  • some or all of the re-liquefied boil-off gas is sent directly to the storage tank (T), when the vessel of this embodiment includes the gas-liquid separator 170 Partially or wholly reliquefied boil-off gas is sent to the gas-liquid separator 170.
  • the gas separated by the gas-liquid separator 170 is combined with the boil-off gas discharged from the storage tank T and sent to the boil-off gas heat exchanger 110, and the liquid separated by the gas-liquid separator 170 is stored in the storage tank ( Sent to T).
  • the boil-off gas circulating through the refrigerant cycle is compressed by the compressor 120 and cooled by the cooler 130 and then passed through the fourteenth valve 303 to the refrigerant heat exchanger 140.
  • the evaporated gas sent to the refrigerant heat exchanger 140 is first heat-exchanged by the refrigerant heat exchanger 140, cooled, and then sent to the refrigerant pressure reducing device 160 to expand secondly. And cooled.
  • the evaporated gas passing through the refrigerant pressure reducing device 160 is sent to the refrigerant heat exchanger 140 again, and passes through the evaporative gas heat exchanger 110, and then evaporates supplied to the refrigerant heat exchanger 140 along the return line L3.
  • the boil-off gas used as the refrigerant in the refrigerant heat exchanger 140 flows along the recycle line L5 and branches to the first additional line L6, and then again to the second additional line. It branches to L7 and is sent to the 1st supply line L1 through 12th valve 301.
  • the boil-off gas sent to the first supply line L1 is sent to the compressor 120 again and repeats the above-described series of processes.
  • the spare compressor 122 or the spare cooler 132 fails while the refrigerant cycle of the ship of the present embodiment is operated as the second closed loop, the third valve 193, the fourth valve 194, and the twelfth valve
  • the 301, the 14th valve 303, and the 15th valve 304 are closed, the first valve 191 and the second valve 192 are opened, and after being discharged from the storage tank T, the evaporative gas heat exchanger.
  • the boil-off gas passing through the 110 is supplied to the fuel demand 180 through the first valve 191, the compressor 120, the cooler 130, and the second valve 192.
  • the spare compressor 122 or the spare cooler 132 is broken while the refrigerant cycle of the ship of the present embodiment is operating in the second closed loop, it is necessary to re-liquefy a part of the boil-off gas.
  • a part of the boil-off gas may be subjected to the reliquefaction process along the return line (L3).
  • the ninth valve 201 and the fourteenth valve ( 303 may be opened, or the twelfth valve 301 and the fourteenth valve 303 may be opened to operate the system.
  • the flow rate of the refrigerant sent to the refrigerant heat exchanger 140 can be flexibly adjusted in consideration of the amount of reliquefaction and the amount of boil-off gas required by the fuel demand 180.
  • the amount of boil-off gas in the fuel demand unit 180 is small, increasing the flow rate of the refrigerant sent to the refrigerant heat exchanger 140 may increase the reliquefaction efficiency and the amount of reliquefaction. That is, when the refrigerant cycle is operated in an open loop, the evaporation gas having a flow rate exceeding the capacity of the redundant compressor 122 may be supplied to the refrigerant heat exchanger 140.
  • the boil-off gas discharged from the storage tank T passes through the boil-off gas heat exchanger 110 and then branches into two streams, some of which are passed through the first valve 191 to the compressor 120, and some of It is sent to the spare compressor 122 via the three valve (193).
  • the boil-off gas sent to the compressor 120 is compressed by the compressor 120 and cooled by the cooler 130, and then some passes through the thirteenth valve 302 and the sixth valve 196 to the refrigerant heat exchanger 140. ), The other part is passed through the second valve 192 to the fuel demand 180, the other part is passed to the boil-off gas heat exchanger 110 through the fifth valve (195).
  • the boil-off gas sent to the spare compressor 122 is compressed by the spare compressor 122 and cooled by the spare cooler 132, and then a part of the boil-off gas is sent to the refrigerant heat exchanger 140 through the sixth valve 196.
  • the remaining part branches into two after passing the thirteenth valve 302.
  • one of the two branched flows is supplied to the fuel demand 180 through the second valve 192 and the remaining flows. Is sent to the boil-off gas heat exchanger (110) via the fifth valve (195).
  • the evaporated gas compressed by the compressor 120 and the evaporated gas separated by the extra compressor 122 are separated and described, but the evaporated gas compressed by the compressor 120 is described. And the boil-off gas separated by the extra compressor 122 are combined to be sent to the refrigerant heat exchanger 140, the fuel demand 180, and the boil-off gas heat exchanger 110.
  • the boil-off gas sent to the refrigerant heat exchanger 140 through the sixth valve 196 is first heat-exchanged and cooled in the refrigerant heat exchanger 140, and is secondly expanded and cooled by the refrigerant pressure reducing device 160 and then again. It is supplied to the refrigerant heat exchanger (140). After passing through the refrigerant pressure reducing device 160, the boil-off gas supplied to the refrigerant heat exchanger 140 passes through the boil-off gas heat exchanger 110 and then is supplied to the refrigerant heat exchanger 140 along the return line L3. Boil off gas; And a boil-off gas supplied from the compressor 120 or the extra compressor 122 to the refrigerant heat exchanger 140 after passing through the sixth valve 196.
  • the boil-off gas used as the refrigerant in the refrigerant heat exchanger 140 is sent to the first supply line L1 through the ninth valve 201 and discharged from the storage tank T. After the evaporated gas heat exchanger 110 is joined with the evaporated gas, the above-described series of processes are repeated.
  • the boil-off gas sent to the boil-off gas heat exchanger 110 along the return line L3 is first cooled in the boil-off gas heat exchanger 110 and secondly cooled in the refrigerant heat exchanger 140, followed by a first pressure reducing device ( 150) to re-liquefy some or all of it.
  • the vessel of this embodiment does not include the gas-liquid separator 170, some or all of the re-liquefied boil-off gas is sent directly to the storage tank (T), when the vessel of this embodiment includes the gas-liquid separator 170 Partially or wholly reliquefied boil-off gas is sent to the gas-liquid separator 170.
  • the gas separated by the gas-liquid separator 170 is combined with the boil-off gas discharged from the storage tank T and sent to the boil-off gas heat exchanger 110, and the liquid separated by the gas-liquid separator 170 is stored in the storage tank ( Sent to T).
  • the first valve 191, the fifth valve 195, the sixth valve 196, And a third valve 193, a spare compressor 122, and a spare cooler 132 by closing the ninth valve 201 and passing through the boil-off gas heat exchanger 110 after being discharged from the storage tank T. ), The thirteenth valve 302, and the second valve 192 to be supplied to the fuel demand 180.
  • the fifth valve 195 is opened. Part of the boil-off gas may be subjected to the reliquefaction process along the return line (L3).
  • the ninth valve 201 and the fourteenth valve 303 may be opened, or the tenth valve 202 and the fourteenth valve 303 may be opened to operate the system.
  • the first valve 191, the second valve 192, the third valve 193, the fifth valve 195, the sixth valve 196 And the ninth valve 201 are opened, and the fourth valve 194, the tenth valve 202, the twelfth valve 301, the thirteenth valve 302, the fourteenth valve 303, and the fifteenth valve ( 304) close.
  • the fourth valve 194 the tenth valve 202, the twelfth valve 301, the thirteenth valve 302, the fourteenth valve 303, and the fifteenth valve ( 304) close.
  • the boil-off gas discharged from the storage tank T passes through the boil-off gas heat exchanger 110 and then branches into two flows, part of which is passed through the first valve 191 to the compressor 120, and the other part of the boil-off gas. It is sent to the spare compressor 122 via the three valve (193).
  • the boil-off gas sent to the compressor 120 is compressed by the compressor 120 and cooled by the cooler 130, and then some are passed through the second valve 192 to the fuel demand 180, and others are
  • the fifth valve 195 is passed to the boil-off gas heat exchanger (110).
  • the boil-off gas sent to the spare compressor 122 is compressed by the spare compressor 122 and cooled by the spare cooler 132, and then passed to the refrigerant heat exchanger 140 through the sixth valve 196.
  • the boil-off gas compressed by the extra compressor 122 and then passed through the sixth valve 196 to the refrigerant heat exchanger 140 is first heat-exchanged by the refrigerant heat exchanger 140 to be cooled, and the refrigerant pressure reducing device 160 is provided. After the second expansion by the cooling to be supplied to the refrigerant heat exchanger 140 again, passing through the boil-off gas heat exchanger 110, the evaporated gas supplied to the refrigerant heat exchanger 140 along the return line (L3); And a boil-off gas compressed by the extra compressor 122 and then passed through the sixth valve 196 to the refrigerant heat exchanger 140.
  • the boil-off gas used as the refrigerant in the refrigerant heat exchanger 140 is sent to the first supply line L1 through the ninth valve 201 and discharged from the storage tank T. After the evaporated gas heat exchanger 110 is joined with the evaporated gas, the above-described process is repeated.
  • the boil-off gas which is compressed by the compressor 120 and then sent to the boil-off gas heat exchanger 110 along the return line L3, is first cooled in the boil-off gas heat exchanger 110, and then cooled in the refrigerant heat exchanger 140. After cooling by the car, the first pressure reducing device 150 is expanded to re-liquefy a part or all of the liquid.
  • the vessel of this embodiment does not include the gas-liquid separator 170, some or all of the re-liquefied boil-off gas is sent directly to the storage tank (T), when the vessel of this embodiment includes the gas-liquid separator 170 Partially or wholly reliquefied boil-off gas is sent to the gas-liquid separator 170.
  • the gas separated by the gas-liquid separator 170 is combined with the boil-off gas discharged from the storage tank T and sent to the boil-off gas heat exchanger 110, and the liquid separated by the gas-liquid separator 170 is stored in the storage tank ( Sent to T).
  • the compressor 120 or the cooler 130 When the compressor 120 or the cooler 130 is broken while the refrigerant cycle of the ship of the present embodiment is operated in an independent open loop, the first valve 191, the fifth valve 195, and the sixth valve 196 are broken down. And the ninth valve 201, the thirteenth valve 302, the evaporated gas passing through the evaporative gas heat exchanger 110 after being discharged from the storage tank T, the third valve 193, The spare compressor 122, the spare cooler 132, the thirteenth valve 302, and the second valve 192 are supplied to the fuel demand 180.
  • the fifth valve 195 is opened if it is necessary to reliquefy a part of the boil-off gas. , Part of the boil-off gas may be subjected to the reliquefaction process along the return line (L3).
  • the sixth valve 196 and the ninth valve 201 may be opened, or sixth valve 196 and tenth valve 202 may be opened to operate the system.
  • FIG. 7 is a configuration diagram schematically showing a boil-off gas treatment system according to a sixth embodiment of the present invention.
  • the ship of the sixth embodiment shown in FIG. 7 has a second spare compressor 126, a second spare cooler 136, a third supply line L6, and a second supply compressor compared to the ship of the third embodiment shown in FIG. 4. 1 further includes an additional line L7, a second additional line L8, and ninth to fourteenth valves 201, 202, 203, 204, 205, and 206, and corrects some lines through which the fluid flows. Differences exist in the following, and the following description focuses on the differences. Detailed descriptions of the same members as those of the ship of the third embodiment are omitted.
  • the vessel of the present embodiment like the third embodiment, has a boil-off gas heat exchanger 110, a first valve 191, a compressor 120, a cooler 130, and a second valve 192.
  • And 150 the first pressure reducing device.
  • the ninth valve 201 is installed on the recirculation line (L5); A third supply line L6 branched from the second supply line L2 and connected to the recirculation line L5; A second extra compressor 126 installed on the third supply line L6 to compress the boil-off gas discharged from the storage tank T; A second extra cooler 136 installed downstream of the second extra compressor 126 of the third supply line L6 to lower the temperature of the boil-off gas compressed by the second extra compressor 126; A tenth valve 202 installed on the third supply line L6 upstream of the second redundant compressor 126; A twelfth valve 204 installed on the recirculation line L5 between the second supply line L2 and the third supply line L6; A first additional line L7 connecting between the recirculation line L5 and the third supply line L6; A second additional line L8 connecting between the first additional line L7 and the second supply line L2; A thirteenth valve 205 installed on the first additional line L7; And a fourteenth valve
  • the ship of this embodiment is provided on the recirculation line L5 between the first supply line L1 and the second supply line L2, unlike the third embodiment selectively includes a sixth valve.
  • the sixth valve 196 is essentially included.
  • the ship of the present embodiment unlike the third embodiment, the second supply line (L2) downstream of the first redundant compressor 122 is connected to the recirculation line (L5), not the first supply line (L1). do. That is, the recirculation line L5 of the present embodiment is branched from the first supply line L1 and sequentially connected to the downstream end of the second supply line L2 and the downstream end of the third supply line L6. Then extend toward the refrigerant heat exchanger 140.
  • the storage tank T of the present embodiment stores the liquefied gas such as liquefied natural gas and liquefied ethane gas inside, and discharges the boil-off gas to the outside when the internal pressure is higher than the predetermined pressure.
  • the boil-off gas discharged from the storage tank T is sent to the boil-off gas heat exchanger 110.
  • the boil-off gas heat exchanger 110 of the present embodiment uses the boil-off gas discharged from the storage tank T as a refrigerant and goes to the boil-off gas heat exchanger 110 along the return line L3. Cool the sent boil-off gas. That is, the boil-off gas heat exchanger 110 recovers the cold heat of the boil-off gas discharged from the storage tank T and transfers the collected cold heat to the boil-off gas sent to the boil-off gas heat exchanger 110 along the return line L3.
  • a fifth valve 195 may be installed on the return line L3 to control the flow rate and opening and closing of the boil-off gas.
  • the compressor 120 of the present embodiment is installed on the first supply line L1 to compress the boil-off gas discharged from the storage tank T, and the first extra compressor 122 of the present embodiment. As in the third embodiment,) is installed in parallel with the compressor 120 on the second supply line (L2) to compress the boil-off gas discharged from the storage tank (T).
  • the second spare compressor 126 of the present embodiment is installed in parallel with the compressor 120 and the first spare compressor 122 on the third supply line (L6), the evaporated gas discharged from the storage tank (T) Compress it.
  • the compressor 120, the first spare compressor 122, and the second spare compressor 126 may be compressors having the same performance and may be multistage compressors, respectively.
  • the ship of this embodiment includes not only the first spare compressor 122 but also the second spare compressor 126, so that a compressor having a small capacity can be used, which is economical.
  • the compressor 120, the first spare compressor 122, and the second spare compressor 126 have the same capacity, when one of them fails, the other needs to act as a failed compressor (or spare compressor).
  • a compressor needs 150 capacities in total to process boil-off gas
  • compressors having 50 capacities of 50 units each rather than 75 compressors and one extra compressor are installed. And the installation of two spare compressors are much less expensive.
  • the ship of the present embodiment by including an extra compressor, can process the same or more flow rate of boil-off gas at a lower cost.
  • the ship of the present embodiment since the ship of the present embodiment includes not only the first spare compressor 122 but also the second spare compressor 126, it is possible to operate a more detailed and flexible system in accordance with the operating speed of the ship.
  • the amount of liquefied gas in the storage tank (T) is large, the amount of generated evaporated gas increases, and if the operating speed of the vessel is slow, the amount of evaporated gas used in the fuel demand unit 180 decreases, so that the amount of evaporated gas to be reliquefied is stored.
  • the greater the amount of liquefied gas in the tank T the higher the operating speed of the vessel, the lower the amount of liquefied gas in the storage tank T, and the lower the operating speed of the vessel.
  • the amount of liquefied gas in the storage tank T is fluid, the amount of liquefied gas in the storage tank T is large, for example, when the liquefied gas carrier is loaded with the liquefied gas at the production destination and directed to the demand destination.
  • the amount of the liquefied gas in the storage tank (T) for example, when the ship is operating at high speed (about 18 to 19 knots), only one of the three compressors (120, 122, 126) is used, The system can be operated in such a way that when the vessel is operating at low speed (approximately 13 to 14 knots), two are used, and when the vessel is anchored, all three are used.
  • the time at which the ship operates at high speed is usually shorter than the time at which the ship operates at low speed or anchored, according to the present embodiment, the time required for all the compressors installed in the ship to be minimized is minimized. You can fully secure the concept.
  • the compressor 120, the first spare compressor 122, and the second spare compressor 126 of the present exemplary embodiment may compress the boil-off gas to a pressure required by the fuel demand 180.
  • some of the high pressures are compressed after compressing the boil-off gas in accordance with a required pressure of an engine requiring higher pressure (hereinafter, referred to as a 'high pressure engine'). It can be supplied to the engine, and the other part can be supplied to the low pressure engine after being depressurized by a pressure reducing device installed upstream of the engine requiring a lower pressure (hereinafter referred to as a 'low pressure engine').
  • the fuel demand unit 180 is compressed to a high pressure or higher than the pressure required by the fuel demand unit 180, By installing a decompression device upstream, the pressure of the boil-off gas compressed to high pressure may be lowered to the pressure required by the fuel demand unit 180 and then supplied to the fuel demand unit 180.
  • the vessel of this embodiment can use the boil-off gas compressed by the first spare compressor 122 and the second spare compressor 126 as a refrigerant for additionally cooling the boil-off gas in the refrigerant heat exchanger 140, thereby re-liquefying efficiency. And the amount of reliquefaction can be increased.
  • the cooler 130 of this embodiment is installed downstream of the compressor 120 to cool the boil-off gas that has passed through the compressor 120 and has risen in pressure as well as in temperature.
  • the cooler 132 is installed downstream of the first extra compressor 122 to cool the evaporated gas that has passed through the first extra compressor 122 and has risen in temperature as well as pressure.
  • the second extra cooler 136 of the present embodiment is installed downstream of the second extra compressor 126 to cool the evaporated gas passing through the second extra compressor 126 and having risen in pressure as well as temperature.
  • the fuel demand 180 of the present embodiment may be any one of a ME-GI engine, an X-DF engine, a DFDE, and a gas turbine engine, as in the third embodiment, and includes a compressor 120 and a first spare compressor 122.
  • the second spare compressor 126 can compress the boil-off gas to a pressure of approximately 150bar to 400bar when the fuel demand 180 is a ME-GI engine
  • the boil-off gas when the fuel demand 180 is DFDE May be compressed to a pressure of approximately 6.5 bar
  • the boil-off gas may be compressed to a pressure of approximately 16 bar.
  • a fifteenth valve 207 may be installed to control the flow rate and opening and closing of the boil-off gas supplied to the fuel demand unit 180.
  • One side of the third supply line L6 of the present embodiment is connected to the second supply line L2 upstream of the third valve 193, and the other side thereof is connected to the recirculation line L5 upstream of the twelfth valve 204. Connected.
  • One side of the first additional line (L7) of the present embodiment after being expanded by the refrigerant pressure reducing device 160, and sends the evaporated gas passed through the refrigerant heat exchanger 140 to the first supply line (L1), recirculation line ( L5), and the other side is connected to a third supply line L6 between the tenth valve 202 and the second spare compressor 126.
  • One side of the second additional line L8 of the present embodiment is connected to the first additional line L7 upstream of the thirteenth valve 205, and the other side thereof is the third valve 193 and the first spare compressor 122. It is connected to the second supply line (L2) in between.
  • the recirculation line L5 meets the first supply line L1 upstream of the compressor 120 and the spare compressors 122 and 126, and the recirculation line L5 1 is installed on the recirculation line (L5) between the point where the additional line (L7) meets, to regulate the flow rate and opening and closing of the boil-off gas.
  • Refrigerant heat exchanger 140 of the present embodiment is supplied to the boil-off gas heat exchanger 110 along the return line (L3), and the boil-off gas cooled by the boil-off gas heat exchanger (110) Cool additionally.
  • the evaporated gas discharged from the storage tank T is further cooled not only in the evaporation gas heat exchanger 110 but also in the refrigerant heat exchanger 140, so that the temperature is lower. Since it can be supplied to the first decompression device 150, the reliquefaction efficiency and the amount of reliquefaction are increased.
  • the refrigerant pressure reducing device 160 expands the evaporated gas passing through the refrigerant heat exchanger 140 and sends it to the refrigerant heat exchanger 140 in the same manner as in the third embodiment.
  • the first pressure reducing device 150 of the present embodiment is installed on the return line L3 to supply the boil-off gas cooled by the boil-off gas heat exchanger 110 and the refrigerant heat exchanger 140. Inflate.
  • the first pressure reducing device 150 of the present embodiment includes all means capable of expanding and cooling the boil-off gas, and may be an expansion valve such as a Joule-Thomson valve or an expander.
  • the vessel of the present embodiment is installed on the return line L3 downstream of the first pressure reducing device 150 and separates the gas-liquid mixture discharged from the first pressure reducing device 150 into gas and liquid.
  • Gas-liquid separator 170 may be included.
  • the vessel of this embodiment does not include the gas-liquid separator 170
  • the liquid or gaseous-mixed evaporated gas that has passed through the first decompression device 150 is directly sent to the storage tank T.
  • the vessel of the present embodiment includes the gas-liquid separator 170
  • the boil-off gas passing through the first pressure reducing device 150 is sent to the gas-liquid separator 170 to separate the gas phase and the liquid phase.
  • the liquid separated by the gas-liquid separator 170 is returned to the storage tank T along the return line L3, and the gas separated by the gas-liquid separator 170 is separated from the gas-liquid separator 170 by the evaporative gas heat exchanger ( 110 is supplied to the boil-off gas heat exchanger 110 along the gas discharge line L4 extending upstream of the first supply line L1.
  • the vessel of the present embodiment includes the gas-liquid separator 170, like the third embodiment, the seventh valve (197) for controlling the flow rate of the liquid separated by the gas-liquid separator 170 and sent to the storage tank (T) ); And an eighth valve 198 that controls the flow rate of the gas separated by the gas-liquid separator 170 and sent to the boil-off gas heat exchanger 110.
  • the first to fifteenth valves 191, 192, 193, 194, 195, 196, 197, 198, 201, 202, 203, 204, 205, 206, and 207 of the present embodiment directly determine a system operation situation. It may be adjusted manually or may be automatically adjusted to open and close by a preset value.
  • the ship of the present embodiment has a first additional line L7, a second additional line L8, a sixth valve 196, a ninth valve 201, and a twelfth valve 204.
  • a thirteenth valve 205 and a fourteenth valve 206, and the second supply line L2 and the third supply line L6 are configured to be directly connected to the recirculation line L5, thereby
  • the refrigerant cycle may be operated in a closed loop like in the first and second embodiments, and may be operated in an open loop as in the third embodiment.
  • the method of operating the refrigerant cycle in the closed loop and the method of operating in the open loop through the valve adjustment will be described.
  • the evaporated gas compressed by the second spare compressor 126 is used as the refrigerant in the refrigerant heat exchanger 140, and the compressed gas is compressed by the compressor 120.
  • the ship of this embodiment may further include a pipe for introducing nitrogen gas into the refrigerant cycle of the closed loop.
  • the evaporated gas circulating in the closed loop is used as the refrigerant in the refrigerant heat exchanger 140, and the evaporated gas or the first spare compressor 122 that has passed through the compressor 120 is used.
  • the evaporated gas passing through) is not introduced into the refrigerant cycle but is supplied to the fuel demand 180, or is re-liquefied along the return line L3. Therefore, regardless of the amount of reliquefaction and the amount of boil-off gas required by the fuel demand unit 180, the boil-off gas of a constant flow rate is circulated to the refrigerant of the refrigerant heat exchanger 140.
  • the boil-off gas discharged from the storage tank T passes through the boil-off gas heat exchanger 110 and then branches into two flows, and one flow is compressed by the compressor 120 along the first supply line L1 and then cooled. Cooled by 130, the other flow is compressed by the first spare compressor 122 along the second supply line (L2) and then cooled by the first spare cooler (132).
  • the evaporated gas passing through the compressor 120 and the cooler 130 along the first supply line L1 and the first extra compressor 122 and the second extra cooler 136 along the second supply line L2 are connected.
  • the boil-off gas passed through is joined in the recirculation line (L5), part of which is sent to the fuel demand (180), and the other part is sent to the boil-off gas heat exchanger (110) along the return line (L3).
  • the boil-off gas sent to the boil-off gas heat exchanger 110 along the return line L3 is heat-exchanged with the boil-off gas discharged from the storage tank T and then cooled, and further cooled by heat-exchange in the refrigerant heat exchanger 140.
  • the boil-off gas cooled by the boil-off gas heat exchanger 110 and the refrigerant heat exchanger 140 is expanded by the first pressure reducing device 150 to re-liquefy some or all of the boil-off gas.
  • some or all of the re-liquefied boil-off gas is sent directly to the storage tank (T), when the vessel of this embodiment includes the gas-liquid separator 170 Partially or wholly reliquefied boil-off gas is sent to the gas-liquid separator 170.
  • the gas separated by the gas-liquid separator 170 is combined with the boil-off gas discharged from the storage tank T and sent to the boil-off gas heat exchanger 110, and the liquid separated by the gas-liquid separator 170 is stored in the storage tank ( Sent to T).
  • the boil-off gas circulating through the refrigerant cycle is compressed by the second extra compressor 126 and cooled by the second extra cooler 136 and then sent to the refrigerant heat exchanger 140 along the recirculation line L5. .
  • the evaporated gas sent to the refrigerant heat exchanger 140 is first heat exchanged and cooled in the refrigerant heat exchanger 140, and then the refrigerant pressure reducing device 160 It is sent to) and expanded secondly and cooled.
  • the evaporated gas passing through the refrigerant pressure reducing device 160 is sent to the refrigerant heat exchanger 140 again, and passes through the evaporative gas heat exchanger 110, and then evaporates supplied to the refrigerant heat exchanger 140 along the return line L3. gas; And a boil-off gas compressed by the second spare compressor 126 and then supplied to the refrigerant heat exchanger 140 along the recirculation line L5. After passing through the refrigerant pressure reducing device 160, the boil-off gas used as the refrigerant in the refrigerant heat exchanger 140 is sent to the second spare compressor 126 again and repeats the above-described series of processes.
  • the compressor 120 or the cooler 130 fails while the refrigerant cycle of the ship of the present embodiment is operated in the first closed loop, the first valve 191, the second valve 192, and the thirteenth valve 205 ) Is closed, the tenth valve 202 and the twelfth valve 204 are opened, the first extra compressor 122 of the boil-off gas passed through the boil-off gas heat exchanger 110 after being discharged from the storage tank (T) And the boil-off gas passed through the first extra cooler 132 and the boil-off gas passed through the second extra compressor 126 and the second extra cooler 136 may be supplied to the fuel demand 180. .
  • the 9th valve 201 When it is necessary to use the boil-off gas compressed by the 1st spare compressor 122 and the boil-off gas compressed by the 2nd spare compressor 126 as a refrigerant
  • the evaporated gas compressed by the first spare compressor 122 is used as the refrigerant in the refrigerant heat exchanger 140, and the compressed gas is compressed by the compressor 120. Only the first valve 191, the second, to send the bay to the fuel demand 180 or to re-liquefy, and not to drive the second redundant compressor 126 (hereinafter referred to as 'second closed loop').
  • valve 192, the third valve 193, the fourth valve 194, the twelfth valve 204, the fourteenth valve 206, and the fifteenth valve 207 are opened, the sixth valve 196,
  • the ninth valve 201, the tenth valve 202, the eleventh valve 203, and the thirteenth valve 205 drive the system in a closed state.
  • the third valve 193 is closed to supply the boil-off gas to the first extra compressor 122.
  • a closed loop refrigerant cycle is formed, which circulates 206.
  • nitrogen gas may be used as the refrigerant circulating in the closed loop similarly to the case where the refrigerant cycle is operated with the first closed loop.
  • the evaporated gas passing through 120 may not be introduced into the refrigerant cycle, but may be supplied to the fuel demand 180, or may be reliquefied along the return line L3. Therefore, regardless of the amount of reliquefaction and the amount of boil-off gas required by the fuel demand unit 180, the boil-off gas of a constant flow rate is circulated to the refrigerant of the refrigerant heat exchanger 140.
  • the operation of the refrigerant cycle as the second closed loop is suitable when the demand at the fuel demand 180 is somewhat small and the amount of the boil-off gas to be liquefied is relatively small.
  • the boil-off gas discharged from the storage tank T is passed by the boil-off gas heat exchanger 110 and then compressed by the compressor 120 and cooled by the cooler 130, and part of the boil-off gas is sent to the fuel demand 180.
  • the other part is sent to the boil-off gas heat exchanger 110 along the return line (L3).
  • the boil-off gas sent to the boil-off gas heat exchanger 110 along the return line L3 is heat-exchanged with the boil-off gas discharged from the storage tank T and then cooled, and further cooled by heat-exchange in the refrigerant heat exchanger 140.
  • the boil-off gas cooled by the boil-off gas heat exchanger 110 and the refrigerant heat exchanger 140 is expanded by the first pressure reducing device 150 to re-liquefy some or all of the boil-off gas.
  • some or all of the re-liquefied boil-off gas is sent directly to the storage tank (T), when the vessel of this embodiment includes the gas-liquid separator 170 Partially or wholly reliquefied boil-off gas is sent to the gas-liquid separator 170.
  • the gas separated by the gas-liquid separator 170 is combined with the boil-off gas discharged from the storage tank T and sent to the boil-off gas heat exchanger 110, and the liquid separated by the gas-liquid separator 170 is stored in the storage tank ( Sent to T).
  • the boil-off gas circulating through the refrigerant cycle is compressed by the first extra compressor 122 and cooled by the first extra cooler 132, and then passes through the twelfth valve 204 to the refrigerant heat exchanger 140. Is sent. After passing through the first spare compressor 122 and the first spare cooler 132, the evaporated gas sent to the refrigerant heat exchanger 140 is first heat-exchanged by the refrigerant heat exchanger 140, and is then cooled. It is sent to) and expanded secondly and cooled.
  • the evaporated gas passing through the refrigerant pressure reducing device 160 is sent to the refrigerant heat exchanger 140 again, and passes through the evaporative gas heat exchanger 110, and then evaporates supplied to the refrigerant heat exchanger 140 along the return line L3. gas; And a boil-off gas compressed by the first extra compressor 122 and supplied to the refrigerant heat exchanger 140 along the recirculation line L5. After passing through the refrigerant pressure reducing device 160, the boil-off gas used as the refrigerant in the refrigerant heat exchanger 140 is passed through the fourteenth valve 206 to the first redundant compressor 122 to repeat the above-described series of processes. do.
  • the compressor 120 or the cooler 130 breaks down while the refrigerant cycle of the ship of the present embodiment is operated in the second closed loop, the first valve 191, the second valve 192, and the fourteenth valve 206 ), The third valve 193 and the sixth valve 196 are opened, and the boil-off gas passed through the boil-off gas heat exchanger 110 after being discharged from the storage tank T is connected to the third valve 193, The first extra compressor 122, the first extra cooler 132, the fourth valve 194, the sixth valve 196, and the fifteenth valve 207 are supplied to the fuel demand 180.
  • the 9th valve 201 and the 12th valve 204 are opened, or 12th
  • the valve 204 and the fourteenth valve 206 may be opened to operate the system.
  • the evaporated gas compressed by the first spare compressor 122 and the evaporated gas compressed by the second spare compressor 126 are refrigerant in the refrigerant heat exchanger 140.
  • the ninth valve ( 201 is closed, the evaporated gas passing through the first extra compressor 122 and the first extra cooler 132 along the second supply line L2 and the second extra compressor (3) along the third supply line L6 ( 126 and the evaporated gas passing through the second extra cooler 136 are combined and supplied to the refrigerant heat exchanger 140 along the recirculation line L5, and the evaporated gas supplied to the refrigerant heat exchanger 140 is a refrigerant.
  • the pressure reducing device 160 and the refrigerant heat exchanger 140 After passing through the pressure reducing device 160 and the refrigerant heat exchanger 140 again, it branches into two flows again to form a closed loop refrigerant cycle, which is sent to the first spare compressor 122 or the second spare compressor 126. .
  • nitrogen gas may be used as the refrigerant circulating in the closed loop similarly to the case in which the refrigerant cycle is operated in the first closed loop.
  • the evaporated gas passing through 120 may not be introduced into the refrigerant cycle, but may be supplied to the fuel demand 180, or may be reliquefied along the return line L3. Therefore, regardless of the amount of reliquefaction and the amount of boil-off gas required by the fuel demand unit 180, the boil-off gas of a constant flow rate is circulated to the refrigerant of the refrigerant heat exchanger 140.
  • the operation of the refrigerant cycle as the third closed loop is suitable for the case where the demand at the fuel demand 180 is small and the amount of the boil-off gas to be reliquefied is large.
  • the boil-off gas discharged from the storage tank T is passed by the boil-off gas heat exchanger 110 and then compressed by the compressor 120 and cooled by the cooler 130, and part of the boil-off gas is sent to the fuel demand 180.
  • the other part is sent to the boil-off gas heat exchanger 110 along the return line (L3).
  • the boil-off gas sent to the boil-off gas heat exchanger 110 along the return line L3 is heat-exchanged with the boil-off gas discharged from the storage tank T and then cooled, and further cooled by heat-exchange in the refrigerant heat exchanger 140.
  • the boil-off gas cooled by the boil-off gas heat exchanger 110 and the refrigerant heat exchanger 140 is expanded by the first pressure reducing device 150 to re-liquefy some or all of the boil-off gas.
  • some or all of the re-liquefied boil-off gas is sent directly to the storage tank (T), when the vessel of this embodiment includes the gas-liquid separator 170 Partially or wholly reliquefied boil-off gas is sent to the gas-liquid separator 170.
  • the gas separated by the gas-liquid separator 170 is combined with the boil-off gas discharged from the storage tank T and sent to the boil-off gas heat exchanger 110, and the liquid separated by the gas-liquid separator 170 is stored in the storage tank ( Sent to T).
  • the boil-off gas circulating through the refrigerant cycle is partially compressed by the first extra compressor 122 and cooled by the first extra cooler 132 to be sent to the recirculation line L5, and the other part is the second extra. Compressed by the compressor 126 and cooled by the second extra cooler 136 and sent to the recirculation line (L5).
  • the boil-off gas compressed by the first spare compressor 122 and the boil-off gas compressed by the second spare compressor 126 are joined in the recirculation line L5 and sent to the refrigerant heat exchanger 140, and the recirculation line L5.
  • the evaporated gas sent to the refrigerant heat exchanger 140 along the c) is first heat exchanged and cooled in the refrigerant heat exchanger 140 and then sent to the refrigerant pressure reducing device 160 to be second expanded and cooled.
  • the evaporated gas passing through the refrigerant pressure reducing device 160 is sent to the refrigerant heat exchanger 140 again, and passes through the evaporative gas heat exchanger 110, and then evaporates supplied to the refrigerant heat exchanger 140 along the return line L3. gas; And an evaporated gas supplied to the refrigerant heat exchanger 140 along the recirculation line L5.
  • the evaporated gas used as the refrigerant in the refrigerant heat exchanger 140 is branched into two parts and then sent to the first spare compressor 122 or the second spare compressor 126. Repeat the process.
  • the compressor 120 or the cooler 130 fails while the refrigerant cycle of the ship of the present embodiment is operated in the third closed loop, for example, the first valve 191 and the second valve 192 are closed, The sixth valve 196 and the ninth valve 201 are opened to partially flow the combined flow of the boil-off gas compressed by the first spare compressor 122 and the boil-off gas compressed by the second spare compressor 126.
  • the other part is re-liquefied along the return line (L3), the other part can be operated in a way to use as a refrigerant to the refrigerant heat exchanger (140).
  • the ninth valve 201, the tenth valve 202, the eleventh valve 203, the twelfth valve 204, and the fifteenth valve 207 are opened, and the thirteenth valve 205 and the fourteenth valve 206 are opened. Close).
  • the boil-off gas circulating through the refrigerant cycle and the boil-off gas sent to the fuel demand 180 or undergoing reliquefaction along the return line L3 are separated.
  • the boil-off gas compressed by the compressor 120, the boil-off gas compressed by the first spare compressor 122, and the boil-off gas compressed by the second spare compressor 126 are used. Is joined, used as a refrigerant in the refrigerant heat exchanger 140, or sent to the fuel demand 180, or undergoes a reliquefaction process along the return line (L3).
  • the flow rate of the refrigerant sent to the refrigerant heat exchanger 140 may be flexibly adjusted in consideration of the amount of reliquefaction and the amount of boil-off gas at the fuel demand 180.
  • the amount of boil-off gas in the fuel demand unit 180 is small, increasing the flow rate of the refrigerant sent to the refrigerant heat exchanger 140 may increase the reliquefaction efficiency and the amount of reliquefaction.
  • the evaporation gas having a capacity greater than or equal to that of the first spare compressor 122 and the second spare compressor 126 may be stored in the refrigerant heat exchanger. 140, but when the refrigerant cycle is operated in an open loop, the evaporation gas having a flow rate exceeding the capacity of the first extra compressor 122 and the second extra compressor 126 to the refrigerant heat exchanger 140.
  • the boil-off gas discharged from the storage tank T passes through the boil-off gas heat exchanger 110 and then branches into three flows, part of which is sent to the first supply line L1, and another part of the second supply line ( Is sent to L2), and the remaining part is sent to the third supply line (L6).
  • the boil-off gas sent to the first supply line L1 passes through the first valve 191, the compressor 120, the cooler 130, and the second valve 192, and a part thereof includes the sixth valve 196 and the first valve. 12 is passed through valve 204 to refrigerant heat exchanger 140, the other part again diverging in two flows.
  • One stream of the boil-off gas branched into two streams is sent to the fuel demand unit 180, and the other is sent to the boil-off gas heat exchanger 110 along the return line (L3).
  • the boil-off gas sent to the second supply line L2 passes through the third valve 193, the first spare compressor 122, the first extra cooler 132, and the fourth valve 194, and a part of the 12 is passed through the valve 204 to the refrigerant heat exchanger 140, the other part is passed through the sixth valve (196) to the first supply line (L1) and then branched into two flows.
  • One stream of the boil-off gas branched into two streams is sent to the fuel demand unit 180, and the other stream is sent to the boil-off gas heat exchanger 110 along the return line L3.
  • the boil-off gas sent to the third supply line L6 passes through the tenth valve 202, the second extra compressor 126, the second extra cooler 136, and the eleventh valve 203, and a part of the refrigerant is passed through. It is sent to the heat exchanger 140, the other part is passed through the twelfth valve 204 and the sixth valve (196) to the first supply line (L1) and then branched into two flows.
  • One stream of the boil-off gas branched into two streams is sent to the fuel demand unit 180, and the other stream is sent to the boil-off gas heat exchanger 110 along the return line L3.
  • the evaporated gas compressed by the compressor 120 For convenience of description, the evaporated gas compressed by the compressor 120, the evaporated gas compressed by the first extra compressor 122, and the evaporated gas compressed by the second extra compressor 126 have been separately described.
  • the boil-off gas compressed by the compressor 120, the boil-off gas compressed by the first spare compressor 122, and the boil-off gas compressed by the second spare compressor 126 are not separately flowed, but joined.
  • the fuel demand 180, or the boil-off gas heat exchanger 110 To be supplied to the refrigerant heat exchanger 140, the fuel demand 180, or the boil-off gas heat exchanger 110.
  • the line L3 the boil-off gas compressed by the compressor 120, the boil-off gas compressed by the first extra compressor 122, and the boil-off gas compressed by the second extra compressor 126 flow.
  • the evaporated gas sent to the refrigerant heat exchanger 140 along the recirculation line L5 is first heat exchanged and cooled in the refrigerant heat exchanger 140, and is secondly expanded and cooled by the refrigerant pressure reducing device 160, and then again the refrigerant.
  • the heat exchanger 140 is supplied. After passing through the refrigerant pressure reducing device 160, the boil-off gas supplied to the refrigerant heat exchanger 140 passes through the boil-off gas heat exchanger 110 and then is supplied to the refrigerant heat exchanger 140 along the return line L3.
  • the boil-off gas and the boil-off gas supplied to the refrigerant heat exchanger 140 along the recirculation line L5 are used as a refrigerant to cool both.
  • the boil-off gas used as the refrigerant in the refrigerant heat exchanger 140 is supplied to the refrigerant heat exchanger 140 along the recirculation line L5, and then is first cooled in the refrigerant heat exchanger 140, and the refrigerant pressure reducing device ( It is the boil-off gas cooled by secondary by 160.
  • the boil-off gas sent from the compressor 120, the first extra compressor 122, or the second extra compressor 126 along the recirculation line L5 to the refrigerant heat exchanger 140 is connected to the refrigerant reducing device 160.
  • the evaporated gas passed through is first cooled by a refrigerant.
  • the boil-off gas used as the refrigerant in the refrigerant heat exchanger 140 is sent to the first supply line L1 through the ninth valve 201 and discharged from the storage tank T. After the evaporated gas heat exchanger 110 is joined with the evaporated gas, the above-described series of processes are repeated.
  • the boil-off gas sent to the boil-off gas heat exchanger 110 along the return line L3 is first cooled in the boil-off gas heat exchanger 110 and secondly cooled in the refrigerant heat exchanger 140, followed by a first pressure reducing device ( 150) to re-liquefy some or all of it.
  • the vessel of this embodiment does not include the gas-liquid separator 170, some or all of the re-liquefied boil-off gas is sent directly to the storage tank (T), when the vessel of this embodiment includes the gas-liquid separator 170 Partially or wholly reliquefied boil-off gas is sent to the gas-liquid separator 170.
  • the gas separated by the gas-liquid separator 170 is combined with the boil-off gas discharged from the storage tank T and sent to the boil-off gas heat exchanger 110, and the liquid separated by the gas-liquid separator 170 is stored in the storage tank ( Sent to T).
  • the first valve 191 and the second valve 192 are closed to close the first spare compressor ( 122 and only the second redundant compressor 126 can be operated to operate the refrigerant cycle of the open loop.
  • the liquefied gas stored in the storage tank (T) is liquefied natural gas
  • the fuel demand 180 is an X-DF engine
  • a gas-liquid separator (170) For example, the temperature and pressure of the fluid at each point are described as follows.
  • the boil-off gas discharged from the storage tank T and the boil-off gas separated by the gas-liquid separator 170 are combined to be supplied to the boil-off gas heat exchanger 110, and the boil-off gas at the point A is approximately ⁇ 127 ° C. and 1.060 bara.
  • the boil-off gas at point B after the boil-off gas of approximately -127 ° C. and 1.060 bara is heat-exchanged in the boil-off gas heat exchanger 110 with the boil-off gas of about 43 ° C. and 37 bara is approximately 26 ° C., 0.96. may be bara.
  • the boil-off gas may be 0.96 bara at approximately 17 ° C.
  • the boil-off gas approximately 17 ° C., 0.96 bara, is branched into three, one of which is compressed by the compressor 120 and then cooled by the cooler 130, and the other is compressed by the first spare compressor 122. And then is cooled by the first spare cooler 132, the remaining flow is compressed by the second spare compressor 126 and then cooled by the second spare cooler 136, the compressor 120 and the cooler 130 Flow through; A flow through the first spare compressor 122 and the first spare cooler 132; And the evaporated gas at the point D and the evaporated gas at the point H, which are flows at which the flow passing through the second extra compressor 126 and the second extra cooler 136 join, may be approximately 43 ° C. and 37 bara.
  • the boil-off gas at point E after the boil-off gas of approximately 43 ° C. and 37 bara is heat-exchanged in the boil-off gas heat exchanger 110 with the boil-off gas of approximately ⁇ 127 ° C. and 1.060 bara may be approximately ⁇ 92 ° C. and 37 bara.
  • the evaporation gas at point F, after the evaporation gas having approximately ⁇ 92 ° C. and 37 bara has been cooled in the refrigerant heat exchanger 140, may be approximately ⁇ 124 ° C. and 36.60 bara, and has evaporated approximately ⁇ 124 ° C. and 36.60 bara.
  • the evaporated gas at the point G after the gas is expanded by the first pressure reducing device 150 may be -155 ° C and 2.1 bara.
  • the boil-off gas at point I after the boil-off gas having approximately 43 ° C. and 37 bara is first cooled by the refrigerant heat exchanger 140 may be approximately ⁇ 47 ° C. and 36.70 bara, and approximately ⁇ 47 ° C. and 36.70 bara.
  • the boil-off gas at point J after the boil-off gas is cooled by the refrigerant reducing device 160 in a second manner may be approximately -156 ° C and 1.56bara, and the boil-off gas at approximately -156 ° C and 1.56bara is a refrigerant heat exchanger.
  • the evaporated gas at point K after being used as the refrigerant at 140 may be approximately 13 ° C. and 0.96 bara.
  • the vessel of this embodiment is operated by the evaporation gas compressed by the compressor 120, the evaporated gas compressed by the first spare compressor 122, and the second spare compressor 126 while operating the refrigerant cycle in an open loop.
  • the compressed compressed boil-off gas some are used only as the refrigerant of the refrigerant heat exchanger 140, and others are not used as the refrigerant of the refrigerant heat exchanger 140, but are sent to the fuel demand 180 or the return line (L3). It can also be operated independently to undergo a reliquefaction process. Hereinafter, it is called "independent open loop.”
  • the refrigerant cycle of the ship of the present embodiment is operated as an independent open loop
  • the boil-off gas compressed by the first spare compressor 122 and the boil-off gas compressed by the second spare compressor 126 are transferred to the refrigerant heat exchanger 140.
  • the refrigerant is used as a refrigerant and the vaporized gas compressed by the compressor 120 is sent to the fuel demand unit 180 or undergoes a reliquefaction process (hereinafter, referred to as a 'first independent open loop') will be described. Is as follows.
  • the first valve 191, the second valve 192, the third valve 193, the fourth valve 194, the ninth valve ( 201, the tenth valve 202, the eleventh valve 203, the twelfth valve 204, and the fifteenth valve 207 are opened, and the sixth valve 196, the thirteenth valve 205, and the sixth valve 205 are opened.
  • the valve 206 is closed.
  • the boil-off gas discharged from the storage tank T passes through the boil-off gas heat exchanger 110 and then branches into three flows, part of which is sent to the first supply line L1, and another part of the second supply line L2. ) And the remaining part is sent to the third supply line (L6).
  • the boil-off gas sent to the first supply line L1 passes through the first valve 191, the compressor 120, the cooler 130, and the second valve 192, and a part of the boil-off gas is sent to the fuel demand 180. , The other part is sent to the boil-off gas heat exchanger 110 along the return line (L3).
  • the boil-off gas sent to the second supply line L2 passes through the third valve 193, the first spare compressor 122, the first extra cooler 132, and the fourth valve 194, and then the twelfth valve.
  • Pass 204 is sent to the refrigerant heat exchanger 140 along the recycle line (L5).
  • the boil-off gas sent to the third supply line L6 passes through the tenth valve 202, the second extra compressor 126, the second extra cooler 136, and the eleventh valve 203, and then recirculates ( It is sent to the refrigerant heat exchanger 140 along L5).
  • the evaporated gas compressed by the first extra compressor 122 and the evaporated gas compressed by the second extra compressor 126 have been separated and described, but are compressed by the first extra compressor 122.
  • the boil-off gas and the boil-off gas compressed by the second extra compressor 126 are not separately flowed, but are joined in the recirculation line L5 and supplied to the refrigerant heat exchanger 140.
  • the evaporated gas sent to the refrigerant heat exchanger 140 along the recirculation line L5 is first heat exchanged and cooled in the refrigerant heat exchanger 140, and is secondly expanded and cooled by the refrigerant pressure reducing device 160, and then again the refrigerant.
  • the boil-off gas used as the refrigerant in the refrigerant heat exchanger 140 is sent to the first supply line L1 through the ninth valve 201 and discharged from the storage tank T. After the evaporated gas heat exchanger 110 is joined with the evaporated gas, the above-described process is repeated.
  • the boil-off gas which is compressed by the compressor 120 and then sent to the boil-off gas heat exchanger 110 along the return line L3, is first cooled in the boil-off gas heat exchanger 110, and then cooled in the refrigerant heat exchanger 140. After cooling by the car, the first pressure reducing device 150 is expanded to re-liquefy a part or all of the liquid.
  • the vessel of this embodiment does not include the gas-liquid separator 170, some or all of the re-liquefied boil-off gas is sent directly to the storage tank (T), when the vessel of this embodiment includes the gas-liquid separator 170 Partially or wholly reliquefied boil-off gas is sent to the gas-liquid separator 170.
  • the gas separated by the gas-liquid separator 170 is combined with the boil-off gas discharged from the storage tank T and sent to the boil-off gas heat exchanger 110, and the liquid separated by the gas-liquid separator 170 is stored in the storage tank ( Sent to T).
  • the first valve 191 and the second valve 192 are closed and the sixth valve is closed.
  • 196 may be opened so that the refrigerant cycle of the open loop can be operated only by the first spare compressor 122 and the second spare compressor 126.
  • the first valve 191, the second valve 192, and the ninth valve may be operated.
  • the boil-off gas compressed by the first redundant compressor 122 by closing the valve 201, the tenth valve 202, and the twelfth valve 204 and opening the sixth valve 196 and the thirteenth valve 205. May be sent to the fuel demand unit 180 or undergo a reliquefaction process, and the boil-off gas compressed by the second redundant compressor 126 may circulate the refrigerant cycle of the closed loop.
  • the boil-off gas compressed by the second spare compressor 126 is used as the refrigerant of the refrigerant heat exchanger 140 and compressed by the compressor 120.
  • the three valve 193, the fourth valve 194, the sixth valve 196, the ninth valve 201, the tenth valve 202, the eleventh valve 203, and the fifteenth valve 207 are opened.
  • the twelfth valve 204, the thirteenth valve 205, and the fourteenth valve 206 may be closed to operate the system.
  • FIG. 8 is a configuration diagram schematically showing a boil-off gas treatment system according to a seventh embodiment of the present invention.
  • the vessel of the seventh embodiment shown in FIG. 8 includes a boost compressor 124 installed in the return line, compared to the vessel of the third embodiment shown in FIG. 4; And a propulsion cooler 134 installed downstream of the propulsion compressor 124 to further increase the reliquefaction efficiency and reliquefaction amount in the boil-off gas heat exchanger 110, and a ninth valve 201, Further comprising a tenth valve 202 and the first additional line (L6) and modifying some lines through which the boil-off gas flows, it is possible to operate the refrigerant cycle as a closed loop, as in the first and second embodiments, As in the third embodiment, there is a difference in that the system is configured to be able to operate the refrigerant cycle in an open loop, and the following description will focus on the difference. Detailed descriptions of the same members as those of the ship of the third embodiment are omitted.
  • the vessel of the present embodiment like the third embodiment, has a boil-off gas heat exchanger 110, a first valve 191, a compressor 120, a cooler 130, and a second valve 192.
  • the storage tank T of the present embodiment stores the liquefied gas such as liquefied natural gas and liquefied ethane gas inside, and discharges the boil-off gas to the outside when the internal pressure is higher than the predetermined pressure.
  • the boil-off gas discharged from the storage tank T is sent to the boil-off gas heat exchanger 110.
  • the boil-off gas heat exchanger 110 of the present embodiment uses the boil-off gas discharged from the storage tank T as a refrigerant and goes to the boil-off gas heat exchanger 110 along the return line L3. Cool the sent boil-off gas. That is, the boil-off gas heat exchanger 110 recovers the cold heat of the boil-off gas discharged from the storage tank T and transfers the collected cold heat to the boil-off gas sent to the boil-off gas heat exchanger 110 along the return line L3.
  • a fifth valve 195 may be installed on the return line L3 to control the flow rate and opening and closing of the boil-off gas.
  • the compressor 120 of the present embodiment is installed on the first supply line L1 to compress the evaporated gas discharged from the storage tank T, and the extra compressor 122 of the present embodiment , Like the third embodiment, is installed in parallel with the compressor 120 on the second supply line (L2) to compress the boil-off gas discharged from the storage tank (T).
  • Compressor 120 and spare compressor 122 may be a compressor of the same performance, each may be a multi-stage compressor.
  • the compressor 120 and the spare compressor 122 of this embodiment can compress the boil-off gas to the pressure required by the fuel demand 180 as in the third embodiment.
  • some of the high pressures are compressed after compressing the boil-off gas in accordance with a required pressure of an engine requiring higher pressure (hereinafter, referred to as a 'high pressure engine'). It can be supplied to the engine, and the other part can be supplied to the low pressure engine after being depressurized by a pressure reducing device installed upstream of the engine requiring a lower pressure (hereinafter referred to as a 'low pressure engine').
  • the boil-off gas is supplied to the fuel demand unit 180 by the compressor 120 or the spare compressor 122. Pressure to a pressure higher than the pressure required, and a pressure reducing device is installed upstream of the fuel demand unit 180 to lower the pressure of the boil-off gas compressed to high pressure to the pressure required by the fuel demand unit 180, and then to the fuel demand unit 180. You can also supply.
  • the vessel of this embodiment further includes an eleventh valve 203 which is provided upstream of the fuel demand unit 180 and regulates the flow rate and opening and closing of the boil-off gas sent to the fuel demand unit 180. Can be.
  • the vessel of this embodiment uses the evaporated gas compressed by the extra compressor 122 as a refrigerant for additionally cooling the evaporated gas in the refrigerant heat exchanger 140, so that the reliquefaction efficiency and reliquefaction amount Can increase.
  • the cooler 130 of the present embodiment is installed downstream of the compressor 120 to cool the evaporated gas passing through the compressor 120 and the temperature as well as the pressure
  • the extra cooler of the present embodiment 132, like the third embodiment, is installed downstream of the extra compressor 122 to cool the evaporated gas that has passed through the extra compressor 122 and has risen in temperature as well as pressure.
  • Refrigerant heat exchanger 140 of the present embodiment is supplied to the boil-off gas heat exchanger 110 along the return line (L3), and the boil-off gas cooled by the boil-off gas heat exchanger (110) Cool additionally.
  • the evaporated gas discharged from the storage tank T is further cooled not only in the evaporation gas heat exchanger 110 but also in the refrigerant heat exchanger 140, so that the temperature is lower. Since it can be supplied to the first decompression device 150, the reliquefaction efficiency and the amount of reliquefaction are increased.
  • the refrigerant pressure reducing device 160 expands the evaporated gas passing through the refrigerant heat exchanger 140 and sends it to the refrigerant heat exchanger 140 in the same manner as in the third embodiment.
  • the first pressure reducing device 150 of the present embodiment is installed on the return line L3 to supply the boil-off gas cooled by the boil-off gas heat exchanger 110 and the refrigerant heat exchanger 140. Inflate.
  • the first pressure reducing device 150 of the present embodiment includes all means capable of expanding and cooling the boil-off gas, and may be an expansion valve such as a Joule-Thomson valve or an expander.
  • the vessel of the present embodiment is installed on the return line L3 downstream of the first pressure reducing device 150 and separates the gas-liquid mixture discharged from the first pressure reducing device 150 into gas and liquid.
  • Gas-liquid separator 170 may be included.
  • the vessel of this embodiment does not include the gas-liquid separator 170
  • the liquid or gaseous-mixed evaporated gas that has passed through the first decompression device 150 is directly sent to the storage tank T.
  • the vessel of the present embodiment includes the gas-liquid separator 170
  • the boil-off gas passing through the first pressure reducing device 150 is sent to the gas-liquid separator 170 to separate the gas phase and the liquid phase.
  • the liquid separated by the gas-liquid separator 170 is returned to the storage tank T along the return line L3, and the gas separated by the gas-liquid separator 170 is separated from the gas-liquid separator 170 by the evaporative gas heat exchanger ( 110 is supplied to the boil-off gas heat exchanger 110 along the gas discharge line L4 extending upstream of the first supply line L1.
  • the vessel of the present embodiment includes the gas-liquid separator 170, like the third embodiment, the seventh valve (197) for controlling the flow rate of the liquid separated by the gas-liquid separator 170 and sent to the storage tank (T) ); And an eighth valve 198 that controls the flow rate of the gas separated by the gas-liquid separator 170 and sent to the boil-off gas heat exchanger 110.
  • the propulsion compressor 124 is installed on the return line (L3); And a propulsion cooler 134 installed on the return line L3 downstream of the propulsion compressor 124.
  • the propulsion compressor 124 diverges a portion of the boil-off gas supplied to the fuel demand 180 along the first supply line L1 and sends it to the boil-off gas heat exchanger 110 on the return line L3. Is installed in, to increase the pressure of the boil-off gas supplied to the boil-off gas heat exchanger 110 along the return line (L3).
  • the propulsion compressor 124 may compress the boil-off gas to a pressure below the critical point (approximately 55 bar in the case of methane), may compress it to a pressure above the critical point, and the propulsion compressor 124 of the present embodiment evaporates. If the gas is compressed to above the critical point, it can be compressed to approximately 300 bar.
  • the propulsion cooler 134 of the present embodiment is installed on the return line L3 downstream of the propulsion compressor 124 to lower the temperature of the boil-off gas passing through the propulsion compressor 124 and the temperature as well as the pressure.
  • the ship of the present embodiment further includes a propulsion compressor 124, so that the pressure of the boil-off gas undergoing the reliquefaction process can be increased, thereby increasing the amount of reliquefaction and reliquefaction efficiency.
  • FIG. 10 is a graph showing the temperature value of methane according to the heat flow amount under different pressure, respectively. Referring to FIG. 10, it can be seen that the higher the pressure of the boil-off gas undergoing the reliquefaction process, the higher the efficiency of self-heat exchange. Self- of self-heat exchange means that the low-temperature evaporation gas itself is used as a cooling fluid to exchange heat with the high-temperature evaporation gas.
  • FIG. 10A illustrates the state of each fluid in the refrigerant heat exchanger 140 when the propulsion compressor 124 and the propulsion cooler 134 are not included
  • FIG. 10B illustrates the propulsion compressor. 124 and the propulsion cooler 134 shows the state of each fluid in the refrigerant heat exchanger (140).
  • the uppermost graph I of FIGS. 10A and 10B shows the fluid state at the point I of FIG. 8 supplied to the refrigerant heat exchanger 140 along the recirculation line L5, and the lowermost graph I of FIG. L is a fluid state at point K of FIG. 8 which is supplied back to the refrigerant heat exchanger 140 to be used as a refrigerant after passing through the refrigerant heat exchanger 140 and the refrigerant pressure reducing device 160 along the recirculation line L5.
  • the graph J which is overlapped with the graph K of the middle portion, shows the point F of FIG. 8 which is supplied to the refrigerant heat exchanger 140 along the return line L3 after passing through the boil-off gas heat exchanger 110.
  • the fluid state is shown.
  • the graph L proceeds from left to right with time, and the fluid heat-exchanged with the refrigerant cools the heat from the refrigerant during the heat exchange process. As the temperature is getting lower and lower, the graphs I and J progress from right to left over time.
  • the graph K of the middle part of (a) and (b) of FIG. 10 shows the graph I and the graph J combined. That is, the fluid used as the refrigerant in the refrigerant heat exchanger 140 is drawn as a graph L, and the fluid that is cooled by heat exchange with the refrigerant in the refrigerant heat exchanger 140 is drawn as a graph K.
  • the temperature and heat flow of the fluid supplied to the heat exchanger i.e., points I, K, and F of FIG. 8 are fixed, and the temperature of the fluid used as the refrigerant is higher than the temperature of the fluid to be cooled.
  • LMTD Logarithmic Mean Temperature Difference
  • Logical mean temperature difference is a heat exchange method in which the hot fluid and the low temperature fluid are injected in opposite directions and discharged from the opposite direction.
  • the logarithmic mean temperature difference LMTD is represented by the interval between the low temperature fluid (graph L of FIG. 10) used as the refrigerant and the high temperature fluid (graph K of FIG. 10) cooled by heat exchange with the refrigerant.
  • graph L of FIG. 10 shows that the interval between the graph L and the graph K is narrower.
  • the fluid at the point F of FIG. 8 may be approximately ⁇ 111 ° C. and 20 bar, and includes the propulsion compressor 124.
  • the fluid at point F of FIG. 8 may be approximately ⁇ 90 ° C. and 50 bar.
  • LMTD logarithmic mean temperature difference
  • the ship of the present embodiment includes a propulsion compressor 124, the reliquefaction amount and the reliquefaction efficiency can be increased, and the reliquefaction amount and the reliquefaction efficiency are increased, so that the boil-off gas can be driven without driving the extra compressor 122. Since both cases can be increased, there is an advantage that the frequency of use of the spare compressor 122 can be reduced.
  • the re-liquefaction efficiency can be increased by using the spare compressor 122, the longer the time for driving the spare compressor 122, the weaker the concept of redundancy (redundancy) to prepare for the case where the compressor 120 is broken.
  • the ship of this embodiment can reduce the frequency of use of the spare compressor 122, including the propulsion compressor 124, and can sufficiently secure the concept of redundancy.
  • the propulsion compressor 124 is generally sufficient to have approximately 1/2 of the capacity of the compressor 120 or the spare compressor 122, the propulsion compressor 124 and the compressor (without driving the spare compressor 122) are sufficient.
  • the propulsion compressor 124 and the compressor are sufficient.
  • the ship of this embodiment unlike the third embodiment, includes: a first additional line L6 connecting between the recirculation line L5 and the second supply line L2; A ninth valve 201 installed on the recirculation line L5; And a tenth valve 202 installed on the first additional line L6.
  • the first to eleventh valves 191, 192, 193, 194, 195, 196, 197, 198, 201, 202, and 203 of the present embodiment may be manually adjusted by a person directly determining a system operating situation. It may be automatically adjusted to open and close by a preset value.
  • One side of the first additional line (L6) of the present embodiment after the expansion by the refrigerant pressure reducing device 160, and sends the evaporated gas passed through the refrigerant heat exchanger 140 to the first supply line (L1), recirculation line ( It is connected on the L5, the other side is connected on the second supply line (L2) between the third valve (193) and the spare compressor (122).
  • the ninth valve 201 of the present embodiment has a point where the recirculation line L5 meets the first supply line L1 upstream of the compressor 120 and the spare compressor 122, and the recirculation line L5 is first added. Between the point where it meets the line L6, it is installed on the recirculation line L5.
  • the ship of the present embodiment the second compressor line (L2) downstream of the extra compressor 122 is connected to the recirculation line (L5) rather than the first supply line (L1).
  • the ship of this embodiment can operate the refrigerant cycle as a closed loop as well as an open loop, so that the reliquefaction system can be used more flexibly according to the operating conditions of the ship. How to operate with closed loop and how to operate with open loop will be explained.
  • the third valve 193 is closed to supply the boil-off gas to the extra compressor 122 and the extra cooler.
  • the fourth valve 194 the refrigerant heat exchanger 140, the refrigerant pressure reducing device 160, the refrigerant heat exchanger 140, and the tenth valve 202.
  • the storage tank including the storage tank of the present embodiment may further include a pipe for introducing nitrogen gas into the refrigerant cycle of the closed loop.
  • the refrigerant cycle When the refrigerant cycle is operated as a closed loop, only the boil-off gas circulating in the closed loop is used as the refrigerant in the refrigerant heat exchanger 140, and the boil-off gas passing through the compressor 120 is not introduced into the refrigerant cycle and the fuel demand ( 180 or the reliquefaction process is performed along the return line (L3). Therefore, regardless of the amount of reliquefaction and the amount of boil-off gas required by the fuel demand unit 180, the boil-off gas of a constant flow rate is circulated to the refrigerant of the refrigerant heat exchanger 140.
  • the boil-off gas undergoing the reliquefaction process along the return line L3 is compressed by the propulsion compressor 124 and cooled by the propulsion cooler 134 and then stored by the boil-off heat exchanger 110 by the storage tank T. It is exchanged with the boil-off gas discharged from and cooled.
  • the boil-off gas cooled by the boil-off gas heat exchanger 110 is heat-exchanged in the refrigerant heat-exchanger 140 and further cooled, and then expanded by the first pressure reducing device 150 to liquefy some or all of the boil-off gas.
  • the vessel of this embodiment does not include the gas-liquid separator 170, some or all of the re-liquefied boil-off gas is sent directly to the storage tank (T), when the vessel of this embodiment includes the gas-liquid separator 170 Partially or wholly reliquefied boil-off gas is sent to the gas-liquid separator 170.
  • the gas separated by the gas-liquid separator 170 is combined with the boil-off gas discharged from the storage tank T and sent to the boil-off gas heat exchanger 110, and the liquid separated by the gas-liquid separator 170 is stored in the storage tank ( Sent to T).
  • the boil-off gas circulating through the refrigerant cycle is compressed by the extra compressor 122 and cooled by the extra cooler 132 and then sent to the refrigerant heat exchanger 140 along the recirculation line L5.
  • the evaporated gas sent to the refrigerant heat exchanger 140 is first heat-exchanged by the refrigerant heat exchanger 140, cooled, and then sent to the refrigerant pressure reducing device 160. Inflated and cooled by car.
  • the evaporated gas passing through the refrigerant pressure reducing device 160 is sent to the refrigerant heat exchanger 140 again, and passes through the evaporative gas heat exchanger 110, and then evaporates supplied to the refrigerant heat exchanger 140 along the return line L3. gas; And a boil-off gas compressed by the extra compressor 122 and supplied to the refrigerant heat exchanger 140 along the recirculation line L5. After passing through the refrigerant pressure reducing device 160, the boil-off gas used as the refrigerant in the refrigerant heat exchanger 140 is sent to the spare compressor 122 again and repeats the above-described series of processes.
  • the first valve 191, the second valve 192, and the tenth valve 202 may be The third valve 193 and the sixth valve 196 are opened, and the boil-off gas passed through the boil-off gas heat exchanger 110 after being discharged from the storage tank T is connected to the third valve 193 and the spare compressor.
  • the fuel is supplied to the fuel demand 180 through the 122, the extra cooler 132, the fourth valve 194, and the sixth valve 196.
  • the ninth valve 201 may be opened to operate the system.
  • the first valve 191, the second valve 192, the third valve 193, the fourth valve 194, the sixth valve 196 and The ninth valve 201 is opened and the tenth valve 202 is closed.
  • the boil-off gas circulating through the refrigerant cycle and the boil-off gas sent to the fuel demand 180 or undergoing reliquefaction along the return line L3 are separated.
  • the refrigerant cycle is operated as an open loop, the boil-off gas compressed by the compressor 120 and the boil-off gas compressed by the extra compressor 122 are combined to be used as a refrigerant in the refrigerant heat exchanger 140 or to be fueled. It is sent to the customer 180, or undergoes a reliquefaction process along the return line (L3).
  • the flow rate of the refrigerant sent to the refrigerant heat exchanger 140 may be flexibly adjusted in consideration of the amount of reliquefaction and the amount of boil-off gas at the fuel demand 180.
  • the amount of boil-off gas in the fuel demand unit 180 is small, increasing the flow rate of the refrigerant sent to the refrigerant heat exchanger 140 may increase the reliquefaction efficiency and the amount of reliquefaction.
  • the boil-off gas discharged from the storage tank T passes through the boil-off gas heat exchanger 110 and then branches into two streams, partly to the first supply line L1, and the other part to the second supply line L2. Is sent to.
  • the boil-off gas sent to the first supply line L1 passes through the first valve 191, the compressor 120, the cooler 130, and the second valve 192, and then a part thereof passes through the sixth valve 196. It is sent to the refrigerant heat exchanger 140, and the other part again branches into two flows. One stream of the boil-off gas branched into two streams is sent to the fuel demand unit 180, and the other is sent to the propulsion compressor 124 along the return line (L3).
  • the boil-off gas sent to the second supply line L2 passes through the third valve 193, the spare compressor 122, the extra cooler 132, and the fourth valve 194, and a part thereof is a refrigerant heat exchanger 140. ), The other part is sent to the first supply line (L1) and branches into two flows. One of the evaporated gas branched into two flows is sent to the fuel demand 180, the other flow is sent to the propulsion compressor 124 along the return line (L3).
  • the evaporated gas compressed by the compressor 120 and the evaporated gas compressed by the extra compressor 122 have been described separately, but the evaporated gas and the extra compressor 122 compressed by the compressor 120 are described.
  • the boil-off gas compressed by the gas is not separated and flows, but is joined to and supplied to the refrigerant heat exchanger 140, the fuel demand 180, or the propulsion compressor 124.
  • the evaporated gas sent to the refrigerant heat exchanger 140 along the recirculation line L5 is first heat exchanged and cooled in the refrigerant heat exchanger 140, and is secondly expanded and cooled by the refrigerant pressure reducing device 160, and then again the refrigerant.
  • the heat exchanger 140 is supplied. After passing through the refrigerant pressure reducing device 160, the boil-off gas supplied to the refrigerant heat exchanger 140 passes through the boil-off gas heat exchanger 110 and then is supplied to the refrigerant heat exchanger 140 along the return line L3.
  • the boil-off gas used as the refrigerant in the refrigerant heat exchanger 140 is supplied to the refrigerant heat exchanger 140 along the recirculation line L5, and then is first cooled in the refrigerant heat exchanger 140, and the refrigerant pressure reducing device ( It is the boil-off gas cooled by secondary by 160.
  • the boil-off gas sent from the compressor 120 or the spare compressor 122 to the refrigerant heat exchanger 140 along the recirculation line L5 cools the boil-off gas passed through the refrigerant pressure reducing device 160 as a refrigerant. .
  • the boil-off gas used as the refrigerant in the refrigerant heat exchanger 140 is sent to the first supply line L1 through the ninth valve 201 and discharged from the storage tank T. After the evaporated gas heat exchanger 110 is joined with the evaporated gas, the above-described series of processes are repeated.
  • the boil-off gas sent to the propulsion compressor 124 along the return line L3 is compressed by the propulsion compressor 124, cooled by the propulsion cooler 134, and then sent to the boil-off gas heat exchanger 110.
  • the boil-off gas sent to the boil-off gas heat exchanger 110 is first cooled in the boil-off gas heat exchanger 110, secondly cooled in the refrigerant heat exchanger 140, and then expanded by the first decompression device 150 to partially expand. Or all is liquefied.
  • the vessel of this embodiment does not include the gas-liquid separator 170, some or all of the re-liquefied boil-off gas is sent directly to the storage tank (T), when the vessel of this embodiment includes the gas-liquid separator 170 Partially or wholly reliquefied boil-off gas is sent to the gas-liquid separator 170.
  • the gas separated by the gas-liquid separator 170 is combined with the boil-off gas discharged from the storage tank T and sent to the boil-off gas heat exchanger 110, and the liquid separated by the gas-liquid separator 170 is stored in the storage tank ( Sent to T).
  • the first valve 191, the second valve 192, and the ninth valve 201 are replaced. Closed, the boil-off gas discharged from the storage tank T and passed through the boil-off gas heat exchanger 110, the third valve 193, the spare compressor 122, the extra cooler 132, the fourth valve 194 And a sixth valve 196 to be supplied to the fuel demand 180.
  • the ninth valve 201 may be opened to operate the system.
  • the liquefied gas stored in the storage tank (T) is liquefied natural gas
  • the fuel demand 180 is an X-DF engine
  • a gas-liquid separator (170) For example, the temperature and pressure of the fluid at each point are described as follows.
  • the boil-off gas discharged from the storage tank T and the boil-off gas separated by the gas-liquid separator 170 are combined to be supplied to the boil-off gas heat exchanger 110, and the boil-off gas at the point A is approximately ⁇ 123 ° C. and 1.060 bara.
  • the boil-off gas at point B after the boil-off gas of approximately -123 ° C. and 1.060 bara is heat-exchanged in the boil-off gas heat exchanger 110 with the boil-off gas of about 43 ° C. and 301.1 bara is approximately 40 ° C., 0.96bara.
  • the boil-off gas may be approximately 38 ° C. and 0.96 bara.
  • the boil-off gas approximately 38 ° C., 0.96 bara, is divided into two, one stream is compressed by the compressor 120 and then cooled by the cooler 130, and the other stream is compressed by the spare compressor 122 and then the extra cooler. 132, which flows through the compressor 120 and the cooler 130; And a stream passing through the spare compressor 122 and the spare cooler 132; the combined flow of the evaporated gas at the point D and the evaporated gas at the point I may be approximately 43 ° C. and 17 bara.
  • the boil-off gas at point E after the boil-off gas of approximately 43 ° C. and 17 bara is compressed by the propulsion compressor 124 and cooled by the propulsion cooler 134 may be approximately 43 ° C., 301.1 bara, and approximately 43 ° C.
  • the evaporation gas at the point F after the evaporation gas of 301.1 bara is heat exchanged in the evaporation gas heat exchanger 110 with the evaporation gas of approximately ⁇ 123 ° C. and 1.060 bara may be approximately ⁇ 82 ° C. and 301 bara.
  • the evaporation gas at the point G after the evaporation gas of about -82 ° C and 301bara is cooled in the refrigerant heat exchanger 140 may be about -153 ° C and 300.5bara, and is about -153 ° C and 300.5bara.
  • the boil-off gas at the point H after the boil-off gas is expanded by the first decompression device 150 may be ⁇ 155.6 ° C. and 2.1 bara.
  • the boil-off gas at point J after the boil-off gas of approximately 43 ° C. and 17 bara is first cooled by the refrigerant heat exchanger 140 may be approximately ⁇ 82 ° C. and 16.5 bara, and approximately ⁇ 82 ° C. and 16.5 bara.
  • the boil-off gas at point K after the boil-off gas is cooled by the refrigerant pressure reducing device 160 in a second manner may be approximately -155 ° C and 1.56 bara, and the boil-off gas of approximately -155 ° C and 1.56 bara is a refrigerant heat exchanger.
  • the boil-off gas at point L after being used as a refrigerant at 140 may be approximately 37 ° C. and 0.96 bara.
  • the vessel of the present embodiment operates the refrigerant cycle in an open loop
  • the evaporated gas compressed by the extra compressor 122 is used only as the refrigerant of the refrigerant heat exchanger 140
  • the evaporated gas compressed by the compressor 120 is
  • the spare compressor 122 and the compressor 120 are independently provided so as to be sent to the fuel demand 180 or to undergo a reliquefaction process along the return line L3 and not to be used as the refrigerant of the refrigerant heat exchanger 140. It can also be operated.
  • the refrigerant cycle of the open loop for independently operating the spare compressor 122 and the compressor 120 is referred to as an 'independent open loop'.
  • the refrigerant cycle is operated in an independent open loop, there is an advantage in that the operation of the system is easier than in the open loop.
  • the boil-off gas discharged from the storage tank T passes through the boil-off gas heat exchanger 110 and then branches into two streams, partly to the first supply line L1, and partly to the second supply line L2. Is sent.
  • the boil-off gas sent to the first supply line L1 passes through the first valve 191, the compressor 120, the cooler 130, and the second valve 192, and a part of the boil-off gas is sent to the fuel demand 180. , The other part is sent to the propulsion compressor 124 along the return line (L3).
  • the boil-off gas sent to the second supply line L2 passes through the third valve 193, the spare compressor 122, the extra cooler 132, and the fourth valve 194, and then cools the refrigerant along the recycle line L5. Sent to heat exchanger 140.
  • the boil-off gas which is compressed by the extra compressor 122 and sent to the refrigerant heat exchanger 140 along the recirculation line L5, is first heat-exchanged by the refrigerant heat exchanger 140 and cooled, and is then cooled to the refrigerant pressure reducing device 160. After the second expansion by the cooling to be supplied to the refrigerant heat exchanger 140 again, passing through the boil-off gas heat exchanger 110, the boil-off gas supplied to the refrigerant heat exchanger 140 through the return line (L3); And a boil-off gas compressed by the extra compressor 122 and supplied to the refrigerant heat exchanger 140 along the recirculation line L5.
  • the boil-off gas used as the refrigerant in the refrigerant heat exchanger 140 is sent to the first supply line L1 through the ninth valve 201 and discharged from the storage tank T. After the evaporated gas heat exchanger 110 is joined with the evaporated gas, the above-described process is repeated.
  • the boil-off gas sent to the propulsion compressor 124 along the return line L3 is compressed by the propulsion compressor 124, cooled by the propulsion cooler 134, and then boil-off gas.
  • the boil-off gas sent to the boil-off gas heat exchanger 110 is first cooled in the boil-off gas heat exchanger 110, secondly cooled in the refrigerant heat exchanger 140, and then expanded by the first decompression device 150 to partially expand. Or all is liquefied.
  • the vessel of this embodiment does not include the gas-liquid separator 170, some or all of the re-liquefied boil-off gas is sent directly to the storage tank (T), when the vessel of this embodiment includes the gas-liquid separator 170 Partially or wholly reliquefied boil-off gas is sent to the gas-liquid separator 170.
  • the gas separated by the gas-liquid separator 170 is combined with the boil-off gas discharged from the storage tank T and sent to the boil-off gas heat exchanger 110, and the liquid separated by the gas-liquid separator 170 is stored in the storage tank ( Sent to T).
  • the first valve 191, the second valve 192, and the ninth valve 201 are damaged. 6, the first valve 196 is opened, and the boil-off gas passed through the boil-off gas heat exchanger 110 after being discharged from the storage tank T is connected to the third valve 193, the spare compressor 122, and the extra cooler. 132, the fourth valve 194 and the sixth valve 196 are supplied to the fuel demand 180.
  • the ninth valve 201 may be opened to operate the system.

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PCT/KR2016/003542 2015-06-02 2016-04-05 선박 WO2016195230A1 (ko)

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PL16803585.5T PL3305645T3 (pl) 2015-06-02 2016-04-05 Układ do obróbki gazu bog dla statku
CN201680045491.9A CN107922035B (zh) 2015-06-02 2016-04-05 船舶、船舶的蒸发气体处理***及其方法
SG11201710005RA SG11201710005RA (en) 2015-06-02 2016-04-05 Ship
JP2017562355A JP6899335B2 (ja) 2015-06-02 2016-04-05 船舶
RU2017145881A RU2703370C2 (ru) 2015-06-02 2016-04-05 Судно
US15/579,582 US10399655B2 (en) 2015-06-02 2016-04-05 Ship
EP16803585.5A EP3305645B1 (en) 2015-06-02 2016-04-05 Boil-off gas treatment system for a ship
PH12017502174A PH12017502174A1 (en) 2015-06-02 2017-11-29 Ship

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KR1020150135998A KR101609572B1 (ko) 2015-02-11 2015-09-25 선박
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JP2017525605A (ja) 2017-09-07
JP6285565B2 (ja) 2018-02-28
WO2016195229A1 (ko) 2016-12-08
PL3305644T3 (pl) 2024-05-06

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