EP4035985B1 - Kälterückgewinnungssystem, schiff mit kälterückgewinnungssystem und kälterückgewinnungsverfahren - Google Patents

Kälterückgewinnungssystem, schiff mit kälterückgewinnungssystem und kälterückgewinnungsverfahren

Info

Publication number
EP4035985B1
EP4035985B1 EP20893934.8A EP20893934A EP4035985B1 EP 4035985 B1 EP4035985 B1 EP 4035985B1 EP 20893934 A EP20893934 A EP 20893934A EP 4035985 B1 EP4035985 B1 EP 4035985B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
liquefied gas
heat
working fluid
heat medium
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP20893934.8A
Other languages
English (en)
French (fr)
Other versions
EP4035985A4 (de
EP4035985A1 (de
Inventor
Ryo TAKATA
Akira Kawanami
Eiji Saito
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Marine Machinery and Equipment Co Ltd
Original Assignee
Mitsubishi Heavy Industries Marine Machinery and Equipment Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Marine Machinery and Equipment Co Ltd filed Critical Mitsubishi Heavy Industries Marine Machinery and Equipment Co Ltd
Publication of EP4035985A1 publication Critical patent/EP4035985A1/de
Publication of EP4035985A4 publication Critical patent/EP4035985A4/de
Application granted granted Critical
Publication of EP4035985B1 publication Critical patent/EP4035985B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63J—AUXILIARIES ON VESSELS
    • B63J2/00—Arrangements of ventilation, heating, cooling, or air-conditioning
    • B63J2/12—Heating; Cooling
    • B63J2/14—Heating; Cooling of liquid-freight-carrying tanks
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63J—AUXILIARIES ON VESSELS
    • B63J2/00—Arrangements of ventilation, heating, cooling, or air-conditioning
    • B63J2/12—Heating; Cooling
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
    • B63J—AUXILIARIES ON VESSELS
    • B63J3/00—Driving of auxiliaries
    • B63J3/04—Driving of auxiliaries from power plant other than propulsion power plant
    • 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
    • F17C13/00—Details of vessels or of the filling or discharging of vessels
    • F17C13/10—Arrangements for preventing freezing
    • 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
    • F17C9/04—Recovery of thermal energy
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0037—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the conduits for the other heat-exchange medium also being formed by paired plates touching each other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning
    • 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
    • F17C2223/00—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel
    • F17C2223/04—Handled fluid before transfer, i.e. state of fluid when stored in the vessel or before transfer from the vessel characterised by other properties of handled fluid before transfer
    • F17C2223/042—Localisation of the removal point
    • F17C2223/046—Localisation of the removal point in the liquid
    • 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
    • F17C2225/00—Handled fluid after transfer, i.e. state of fluid after transfer from the vessel
    • F17C2225/01—Handled fluid after transfer, i.e. state of fluid after transfer from the vessel characterised by the phase
    • F17C2225/0107—Single phase
    • F17C2225/0123—Single phase gaseous, e.g. CNG, GNC
    • 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
    • F17C2225/00—Handled fluid after transfer, i.e. state of fluid after transfer from the vessel
    • F17C2225/03—Handled fluid after transfer, i.e. state of fluid after transfer from the vessel characterised by the pressure level
    • F17C2225/035—High pressure, i.e. between 10 and 80 bars
    • 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
    • F17C2227/0135—Pumps
    • 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
    • F17C2227/0302—Heat exchange with the fluid by heating
    • F17C2227/0309—Heat exchange with the fluid by heating using another 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
    • F17C2227/0302—Heat exchange with the fluid by heating
    • F17C2227/0309—Heat exchange with the fluid by heating using another fluid
    • F17C2227/0316—Water heating
    • 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
    • F17C2227/0302—Heat exchange with the fluid by heating
    • F17C2227/0309—Heat exchange with the fluid by heating using another fluid
    • F17C2227/0316—Water heating
    • F17C2227/0318—Water heating using seawater
    • 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
    • F17C2227/0302—Heat exchange with the fluid by heating
    • F17C2227/0309—Heat exchange with the fluid by heating using another fluid
    • F17C2227/0323—Heat exchange with the fluid by heating using another fluid in a closed loop
    • 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
    • F17C2227/0302—Heat exchange with the fluid by heating
    • F17C2227/0327—Heat exchange with the fluid by heating with recovery of heat
    • 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
    • F17C2227/0367—Localisation of heat exchange
    • F17C2227/0388—Localisation of heat exchange separate
    • F17C2227/0393—Localisation of heat exchange separate using a vaporiser
    • 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
    • F17C2260/00—Purposes of gas storage and gas handling
    • F17C2260/03—Dealing with losses
    • F17C2260/031—Dealing with losses due to heat transfer
    • F17C2260/032—Avoiding freezing or defrosting
    • 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
    • F17C2260/00—Purposes of gas storage and gas handling
    • F17C2260/04—Reducing risks and environmental impact
    • F17C2260/046—Enhancing energy recovery
    • 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
    • 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
    • F17C2265/07—Generating electrical power as side effect
    • 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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0033—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for cryogenic applications
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2260/00—Heat exchangers or heat exchange elements having special size, e.g. microstructures
    • F28F2260/02—Heat exchangers or heat exchange elements having special size, e.g. microstructures having microchannels

Definitions

  • the present disclosure relates to a cold energy recovery system installed in a ship which includes a liquefied gas storage device configured to store a liquid liquefied gas, and a cold energy recovery method by the cold energy recovery system.
  • a land LNG (liquefied natural gas) terminal receives and stores liquefied natural gas transported by an LNG carrier. Then, when liquefied natural gas is supplied to a supply destination such as city gas or a thermal power plant, liquefied natural gas is warmed with seawater or the like to be returned to a gas. When liquefied natural gas is vaporized, cryogenic power generation may be performed in which cold energy is recovered as electric power instead of being discarded in seawater (for example, Patent Document 1).
  • a ship which is equipped with an LNG storage facility for storing liquefied natural gas or a regasification facility for regasifying liquefied natural gas, may be moored on sea, and the liquefied natural gas regasifyied by the ship may be sent to a supply destination on shore or a power gauge (floating power plant) on sea via a pipeline.
  • a cryogenic power generation facility Since the ship is less expandable than an onshore facility, in order to install a cryogenic power generation facility, it is important to reduce the size of the cryogenic power generation system, especially a heat exchanger.
  • a heat exchanger As the small heat exchanger, a printed circuit heat exchanger (PCHE), a plate heat exchanger, or the like can be given as an example.
  • WO 2010/007535 A1 relates to the conversion of liquefied natural gas and describes a method of and an apparatus for converting liquefied natural gas (LNG) to a superheated fluid through vaporisation and superheating of the LNG.
  • An LNG facility comprises a thermally-insulated storage tank having a submerged LNG pump. The facility is located aboard a seagoing vessel.
  • the apparatus includes a first main heat exchanger in a series with a second main heat exchanger.
  • the first main heat exchanger is heated by a condensing first heat exchange fluid (propane) flowing in a first heat exchange circuit including a first supplementary heat exchanger for revaporising the first heat exchange fluid and the second main heat exchanger by a condensing second heat exchange fluid flowing in a second heat exchange circuit including a second heat exchanger for vaporising the second heat exchange fluid.
  • the first supplementary heat exchanger may be split and comprise two parallel heat exchange units.
  • the first heat exchange circuit has a turbo-expander intermediate the heat exchange vapour exit from the supplementary heat exchanger and the heat exchanger vapour inlet to the main heat exchanger.
  • GB 2 062 111 A concerns recovering energy from liquefied natural gas.
  • Water is used to warm and vaporise liquefied natural gas (LNG) by means of an intermediate heat exchange medium such as propane, which is circulated round a closed circuit wherein it undergoes liquefaction and vaporisation alternately by heat exchange with the LNG and water in heat exchangers, the vaporised intermediate heat exchange medium from the heat exchanger is expanded through a turbine to drive an electricity generator.
  • LNG liquefied natural gas
  • EP 0 009 387 A1 concerns a process for obtaining energy during the regasification of liquefied gases.
  • the liquefied gas is heated in a cryogenic heat exchanger by indirect heat exchange with a working fluid circulating in a closed cycle and is thereafter further heated by passing it in indirect heat exchange with air to be introduced into a gas turbine.
  • the working fluid passes through a recuperator in which it is heated by indirect heat exchange with expanded working fluid from an expansion turbine.
  • KR 101 792 460 B1 relates to an LNG vaporization method of a vaporizer for an LNG carrier, which vaporizes LNG stored in a storage tank of an LNG carrier and supplies the LNG to an engine.
  • the LNG carrier uses a heat pump system, wherein a heat medium for vaporizing LNG in a vapor state in the vaporizer is heat-exchanged and heated by the heat pump system using seawater or air as a heat source.
  • JP 2017/190829 A refers to a system that integrates a gas supply facility and a cooling facility.
  • the gas supply facility supplies gas obtained by vaporizing low-temperature liquefied gas
  • the cooling facility includes a cooling part, a gas cold recovery part for recovering vaporized cold of the low-temperature liquefied gas, and a cooling cold supply part for supplying the recovered cold to the cooling part.
  • the gas cold recovery part includes a first heat exchanger for exchanging heat between the low-temperature liquefied gas and first brine to vaporize the low-temperature liquefied gas and recovering the vaporized cold in the first brine, a gas cold transportation line for circulating the first brine, and a second heat exchanger disposed on the gas cold transportation line for transmitting the cold from the first brine to the cooling cold supply part.
  • WO 2018/100 486 A1 concerns a heat pump with prime mover in cryogenic applications and refrigerating fluids.
  • a liquefied gas regasification line comprises a vaporization section of said gas, a prime mover, a first heat exchanger operating on the circuit of a first intermediate fluid and a heat pump, said heat pump comprising an evaporator and a condenser, said heat pump operating with a refrigerating fluid which in said evaporator acquires heat from a second intermediate fluid and which in said condenser surrenders heat to a third intermediate fluid, said third intermediate fluid operating a further heat exchanger with which it surrenders heat to the liquefied gas.
  • the prime mover supplies mechanical or electrical energy to said heat pump and thermal energy to said first heat exchanger.
  • Patent Document 1 JP 2017- 180 323 A
  • a temperature of another heat exchange object is lower than a solidifying point of one heat exchange object (for example, seawater)
  • the one heat exchange object is solidified in heat exchange in the heat exchanger, and the solidified heat exchange object may adhere to a surface of the exchanger and block the heat exchanger.
  • a small heat exchanger has a higher risk of blockage of the heat exchanger than a large heat exchanger (for example, a shell tube type heat exchanger), and thus has a problem in reliability.
  • an object of at least one embodiment of the present disclosure is to provide a cold energy recovery system capable of suppressing blockage of the heat exchanger due to solidification of a heat medium, and capable of improving reliability of the cold energy recovery system when the small heat exchanger is used.
  • a cold energy recovery system is a cold energy recovery system installed in a ship which includes a liquefied gas storage device configured to store a liquid liquefied gas, as defined in claim 1.
  • the cold energy recovery system includes a working fluid circulation line which is configured to circulate a working fluid having a lower solidifying point than water, a cold energy recovery device that includes a turbine which is configured to be driven by the working fluid flowing through the working fluid circulation line, a first heat exchanger which is configured to exchange heat between the liquefied gas and the working fluid flowing through the working fluid circulation line, an intermediate heat medium circulation line which is configured to circulate an intermediate heat medium having a lower solidifying point than water, a second heat exchanger disposed downstream of the first heat exchanger on the working fluid circulation line, the second heat exchanger being configured to exchange heat between the working fluid flowing through the working fluid circulation line and the intermediate heat medium flowing through the intermediate heat medium circulation line, and a third heat exchanger which is configured to exchange heat between the intermediate heat medium flowing through the intermediate heat medium circulation line and heating water introduced
  • the cold energy recovery system further comprises a liquefied gas supply line configured to send the liquefied gas from the liquefied gas storage device, and an auxiliary heat exchanger disposed downstream of the first heat exchanger on the liquefied gas supply line, the auxiliary heat exchanger being configured to exchange heat between the liquefied gas flowing through the liquefied gas supply line and a heating medium circulating in the cold energy recovery system, wherein the heating medium is constituted by the intermediate heat medium heated by the third heat exchanger and flowing through the intermediate heat medium circulation line.
  • a cold energy recovery method is a cold energy recovery method by a cold energy recovery system installed in a ship which includes a liquefied gas storage device configured to store a liquid liquefied gas, as defined in claim 8.
  • the cold energy recovery system includes a working fluid circulation line which is configured to circulate a working fluid having a lower solidifying point than water, a cold energy recovery device that includes a turbine which is configured to be driven by the working fluid flowing through the working fluid circulation line, a first heat exchanger which is configured to exchange heat between the liquefied gas and the working fluid flowing through the working fluid circulation line, an intermediate heat medium circulation line which is configured to circulate an intermediate heat medium having a lower solidifying point than water, a second heat exchanger disposed downstream of the first heat exchanger on the working fluid circulation line, the second heat exchanger being configured to exchange heat between the working fluid flowing through the working fluid circulation line and the intermediate heat medium flowing through the intermediate heat medium circulation line, and a third heat exchanger which is configured to exchange heat between the intermediate heat medium flowing through the intermediate heat
  • the cold energy recovery system further comprises a liquefied gas supply line configured to send the liquefied gas from the liquefied gas storage device, and an auxiliary heat exchanger disposed downstream of the first heat exchanger on the liquefied gas supply line, the auxiliary heat exchanger being configured to exchange heat between the liquefied gas flowing through the liquefied gas supply line and a heating medium circulating in the cold energy recovery system, wherein the heating medium is constituted by the intermediate heat medium heated by the third heat exchanger and flowing through the intermediate heat medium circulation line.
  • the cold energy recovery method includes a first heat exchange step of performing heat exchange between the liquefied gas and the working fluid by the first heat exchanger, a second heat exchange step of performing, by the second heat exchanger, heat exchange between the intermediate heat medium and the working fluid that has exchanged heat with the liquefied gas in the first heat exchange step, and a third heat exchange step of performing, by the third heat exchanger, heat exchange between the heating water and the intermediate heat medium that has exchanged heat with the working fluid in the second heat exchange step.
  • a cold energy recovery system which is capable of suppressing blockage of a heat exchanger due to solidification of a heat medium, and is capable of improving reliability of a cold energy recovery system when a small heat exchanger is used.
  • an expression of relative or absolute arrangement such as “in a direction”, “along a direction”, “parallel”, “orthogonal”, “centered”, “concentric” and “coaxial” shall not be construed as indicating only the arrangement in a strict literal sense, but also includes a state where the arrangement is relatively displaced by a tolerance, or by an angle or a distance whereby it is possible to achieve the same function.
  • an expression of an equal state such as “same”, “equal”, and “uniform” shall not be construed as indicating only the state in which the feature is strictly equal, but also includes a state in which there is a tolerance or a difference that can still achieve the same function.
  • an expression of a shape such as a rectangular shape or a tubular shape shall not be construed as only the geometrically strict shape, but also includes a shape with unevenness or chamfered corners within the range in which the same effect can be achieved.
  • FIG. 1 is a schematic configuration diagram schematically showing the configuration of a ship having a cold energy recovery system according to an illustrated example or an embodiment of the present invention.
  • a cold energy recovery system 2 is installed in a ship 1.
  • the ship 1 includes a hull 10, and the cold energy recovery system 2 mounted on the hull 10.
  • the ship 1 further includes a liquefied gas storage device (for example, a liquefied gas tank) 11 mounted on the hull 10.
  • the liquefied gas storage device 11 is configured to store a liquid liquefied gas (for example, liquefied natural gas).
  • the hull 10 internally forms an engine room 15.
  • the engine room 15 is equipped with an engine (for example, a marine diesel engine) 16 for applying a propulsive force to the ship 1.
  • an engine for example, a marine diesel engine
  • the ship 1 can be moved from a liquefied gas supply source to the vicinity of a liquefied gas supply destination.
  • FIG. 2 is a schematic configuration diagram schematically showing the overall configuration of the cold energy recovery system according to the illustrative example, which does not include the auxiliary heat exchanger disposed downstream of the first heat exchanger on the liquefied gas supply line as in the claimed invention.
  • FIG. 3 is a schematic configuration diagram schematically showing the overall configuration of the cold energy recovery system according to the first embodiment of the present invention.
  • FIG. 4 is a schematic configuration diagram schematically showing the overall configuration of the cold energy recovery system according to the second embodiment of the present invention.
  • the cold energy recovery system 2 includes a liquefied gas supply line 3, a working fluid circulation line 4, a cold energy recovery device 41, an intermediate heat medium circulation line 6, a heating water supply line 7, a first heat exchanger 51, a second heat exchanger 52, and a third heat exchanger 53.
  • Each of the liquefied gas supply line 3, the working fluid circulation line 4, the intermediate heat medium circulation line 6, and the heating water supply line 7 includes a flow passage through which a fluid flows.
  • the liquefied gas supply line 3 is configured to send a liquefied gas from the liquefied gas storage device 11.
  • the working fluid circulation line 4 is configured to circulate a working fluid having a lower solidifying point than water.
  • liquefied natural gas LNG
  • propane propane will be described as a specific example of the working fluid.
  • the present disclosure is also applicable to a liquefied gas other than liquefied natural gas, and further is also applicable to a case where a heat medium other than propane is used as the working fluid.
  • the cold energy recovery system 2 includes a liquefied gas pump 31 disposed on the liquefied gas supply line 3, and a working fluid circulation pump 44 disposed on the working fluid circulation line 4.
  • the liquefied gas supply line 3 has one end side 301 connected to the liquefied gas storage device 11, and has another end side 302 which is connected to liquefied gas equipment 12 disposed outside the cold energy recovery system 2.
  • a gas holder see FIG. 1
  • a gas pipe connected to the gas holder, or the like can be given as an example.
  • the liquefied gas stored in the liquefied gas storage device 11 is sent to the liquefied gas supply line 3, flows through the liquefied gas supply line 3 from upstream to downstream, and then is sent to the liquefied gas equipment 12. Further, by driving the working fluid circulation pump 44, the working fluid circulates through the working fluid circulation line 4.
  • the cold energy recovery device 41 includes a turbine 42 configured to be driven by the working fluid flowing through the working fluid circulation line 4.
  • the cold energy recovery device 41 further includes a generator 43 configured to generate electricity by driving the turbine 42.
  • the turbine 42 includes a turbine rotor 421 disposed on the working fluid circulation line 4.
  • the turbine rotor 421 is configured to be rotatable by the working fluid flowing through the working fluid circulation line 4.
  • the cold energy recovery device 41 may not convert a rotational force of the turbine rotor 421 into electric power, but may recover the rotational force as power as it is by a power transmission device (for example, a coupling, a belt, a pulley, or the like).
  • the intermediate heat medium circulation line 6 is configured to circulate an intermediate heat medium having a lower solidifying point than water.
  • the heating water supply line 7 is configured to send heating water introduced from the outside of the cold energy recovery system 2.
  • the "heating water” can be water for heating a heat exchange object as a heat medium in the heat exchanger, and may be water at room temperature.
  • the heating water is preferably water that is easily available in the ship 1 (for example, outboard water such as seawater, cooling water that has cooled an engine of the ship 1, or the like).
  • the cold energy recovery system 2 includes an intermediate heat medium circulation pump 61 disposed on the intermediate heat medium circulation line 6, and a heating water pump 71 disposed on the heating water supply line 7.
  • the heating water supply line 7 has one end side 701 which is connected to a heating water supply source 13 disposed outside the cold energy recovery system 2, and another end side 702 which is connected to a heating water discharge destination 14 disposed outside the cold energy recovery system 2.
  • the heating water pump 71 the heating water is sent from the heating water supply source 13 to the heating water supply line 7, flows through the heating water supply line 7 from upstream to downstream, and then is sent to the heating water discharge destination 14.
  • a water inlet 17 (see FIG. 1 ) provided in the hull 10 to introduce outboard water
  • a cooling water flow passage 18 (see FIG. 1 ) where the cooling water that has cooled the engine of the ship 1 (for example, the engine 16) flows, or the like can be given as an example.
  • a water outlet 19 (see FIG. 1 ) provided in the hull 10 to discharge water outboard, or the like can be given as an example.
  • the intermediate heat medium may be the same type of heat medium as the working fluid, or may be a different type of heat medium.
  • the intermediate heat medium is constituted by propane, and the heating water is constituted by the cooling water (engine jacket water) having cooled the engine.
  • the cooling water draws heat from the engine and has a higher temperature than seawater at room temperature.
  • the intermediate heat medium is constituted by propane, and the heating water is constituted by seawater acquired from the outside of the ship.
  • the intermediate heat medium is constituted by antifreeze (more specifically, glycol water), and the heating water is constituted by seawater acquired from the outside of the ship.
  • FIGs. 2 to 4 each show an example of a temperature and a pressure in each flow passage.
  • the first heat exchanger 51 is configured to exchange heat between the liquefied gas flowing through the liquefied gas supply line 3 and the working fluid flowing through the working fluid circulation line 4.
  • the first heat exchanger 51 forms a liquefied gas flow passage 511 which is disposed on the liquefied gas supply line 3 and through which the liquefied gas flows, and a working fluid flow passage 512 which is disposed on the working fluid circulation line 4 and in which the working fluid flows.
  • the working fluid flow passage 512 is disposed at least partially adjacent to the liquefied gas flow passage 511, and heat exchange is performed between the working fluid flowing through the working fluid flow passage 512 and the liquefied gas flowing through the liquefied gas flow passage 511.
  • the second heat exchanger 52 is configured to exchange heat between the working fluid flowing through the working fluid circulation line 4 and the intermediate heat medium flowing through the intermediate heat medium circulation line 6.
  • the second heat exchanger 52 forms a working fluid flow passage 521 which is disposed on the working fluid circulation line 4 and through which the working fluid flows, and an intermediate heat medium flow passage 522 which is disposed on the intermediate heat medium circulation line 6 and in which the intermediate heat medium flows.
  • the intermediate heat medium flow passage 522 is disposed at least partially adjacent to the working fluid flow passage 521, and heat exchange is performed between the intermediate heat medium flowing through the intermediate heat medium flow passage 522 and the working fluid flowing through the working fluid flow passage 521.
  • the third heat exchanger 53 is configured to exchange heat between the intermediate heat medium flowing through the intermediate heat medium circulation line 6 and the heating water flowing through the heating water supply line 7.
  • the third heat exchanger 53 forms an intermediate heat medium flow passage 531 which is disposed on the intermediate heat medium circulation line 6 and through which the intermediate heat medium flows, and a heating water flow passage 532 which is disposed on the heating water supply line 7 and through which the heating water flows.
  • the heating water flow passage 532 is disposed at least partially adjacent to the intermediate heat medium flow passage 531, and heat exchange is performed between the intermediate heat medium flowing through the heating water flow passage 532 and the working fluid flowing through the intermediate heat medium flow passage 531.
  • the first heat exchanger 51 (more specifically, the liquefied gas flow passage 511) is disposed downstream of the liquefied gas pump 31 on the liquefied gas supply line 3 and upstream of the liquefied gas equipment 12.
  • the liquefied gas pump 31 is disposed downstream of the liquefied gas storage device 11 on the liquefied gas supply line 3.
  • the first heat exchanger 51 (more specifically, the working fluid flow passage 512) is disposed downstream of the turbine 42 on the working fluid circulation line 4 and upstream of the working fluid circulation pump 44.
  • the second heat exchanger 52 (more specifically, the working fluid flow passage 521) is disposed downstream of the working fluid circulation pump 44 on the working fluid circulation line 4 and upstream of the turbine 42. Further, the second heat exchanger 52 (more specifically, the intermediate heat medium flow passage 522) is disposed downstream of the third heat exchanger (more specifically, the intermediate heat medium flow passage 531) on the intermediate heat medium circulation line 6 and upstream of the intermediate heat medium circulation pump 61.
  • the third heat exchanger (more specifically, the heating water flow passage 532) is disposed downstream of the heating water pump 71 on the heating water supply line 7 and upstream of the heating water discharge destination 14.
  • the heating water pump 71 is disposed downstream of the heating water supply source 13 on the heating water supply line 7.
  • the liquid liquefied gas boosted by the liquefied gas pump 31 is sent to the liquefied gas flow passage 511 of the first heat exchanger 51.
  • the heat exchange in the first heat exchanger 51 heats the liquefied gas flowing through the liquefied gas flow passage 511 and cools the working fluid flowing through the working fluid flow passage 512. That is, the cold energy of the liquefied gas flowing through the liquefied gas flow passage 511 is recovered by the working fluid flowing through the working fluid flow passage 512.
  • the heat exchange in the first heat exchanger 51 causes the working fluid flowing through the working fluid flow passage 512 to have the temperature lower than the solidifying point of water (heating water).
  • the intermediate heat medium boosted by the intermediate heat medium circulation pump 61 is sent to the intermediate heat medium flow passage 531 of the third heat exchanger 53. Further, the heating water boosted by the heating water pump 71 is sent to the heating water flow passage 532. The heat exchange in the third heat exchanger 53 heats the intermediate heat medium flowing through the intermediate heat medium flow passage 531.
  • the working fluid boosted by the working fluid the circulation pump 44 after being cooled by the first heat exchanger 51 is sent to the working fluid flow passage 521 of the second heat exchanger 52. Further, the intermediate heat medium heated by the third heat exchanger 53 is sent to the intermediate heat medium flow passage 522.
  • the heat exchange in the second heat exchanger 52 heats the working fluid flowing through the working fluid flow passage 521 and cools the intermediate heat medium flow passage 522.
  • the intermediate heat medium has the lower solidifying point than water, it is possible to suppress solidification during the heat exchange with the low-temperature working fluid in the second heat exchanger.
  • the cold energy recovery system 2 decides a condition of each equipment in the cold energy recovery system 2 such that the intermediate heat medium flowing through the intermediate heat medium circulation line 6 has the temperature higher than the solidifying point of water.
  • the intermediate heat medium flowing through the intermediate heat medium flow passage 531 of the third heat exchanger 53 has a higher temperature than the working fluid flowing through the working fluid flow passage 521 of the second heat exchanger 52.
  • the intermediate heat medium flowing through the intermediate heat medium flow passage 531 has the temperature higher than the solidifying point of water (heating water).
  • the temperature higher than the solidifying point of water is maintained even after the cooling.
  • FIG. 5 is a schematic configuration diagram schematically showing the overall configuration of the cold energy recovery system according a comparative example.
  • a cold energy recovery system 20 according to the comparative example includes the liquefied gas supply line 3, the working fluid circulation line 4, the cold energy recovery device 41, the heating water supply line 7, and the first heat exchanger 51. Then, the cold energy recovery system 20 further includes a heat exchanger 50 configured to exchange heat between the working fluid flowing through the working fluid circulation line 4 and the heating water flowing through the heating water supply line 7.
  • the liquefied gas is constituted by liquefied natural gas
  • the working fluid is constituted by R1234ZE
  • the heating water the heating water is constituted by seawater acquired from the outside of the ship.
  • FIG. 5 shows an example of the temperature and the pressure in each flow passage.
  • the heat exchanger 50 forms a working fluid flow passage 501 disposed at a position corresponding to the above-described second heat exchanger 52 (working fluid flow passage 521) on the working fluid circulation line 4, and a heating water flow passage 502 disposed at a position corresponding to the above-described third heat exchanger 53 (heating water flow passage 532) on the heating water supply line 7.
  • the heating water flow passage 502 is disposed at least partially adjacent to the working fluid flow passage 501, and heat exchange is performed between the heating water flowing through the heating water flow passage 502 and the working fluid flowing through the working fluid flow passage 501.
  • the working fluid flowing through the working fluid flow passage 501 has a temperature lower than the solidifying point of water (heating water) like the working fluid flowing through the working fluid flow passage 521.
  • the heating water is solidified by the heat exchange between the working fluid and the heating water in the heat exchanger 50, the solidified heating water may freeze to the heating water flow passage 502 of the heat exchanger 50, and may block the heat exchanger 50.
  • the cold energy recovery system 2 includes the above-described working fluid circulation line 4, the cold energy recovery device 41 including the turbine 42 described above, and the above-described intermediate heat medium circulation line 6, the above-described first heat exchanger 51, the above-described second heat exchanger 52, and the above-described third heat exchanger 53.
  • the cold energy recovery system 2 at least includes the intermediate heat medium circulation line 6, the second heat exchanger 52, and the third heat exchanger 53.
  • the heating water and the working fluid circulating through the working fluid circulation line 4 indirectly exchange heat via the intermediate heat medium circulating through the intermediate heat medium circulation line 6, making it possible to suppress solidification of the heat medium (the intermediate heat medium, the heating water) during the heat exchange.
  • the solidified heat medium freezes to the heat exchanger (the second heat exchanger 52, the third heat exchanger 53) and blocks the heat exchanger.
  • the working fluid circulating through the working fluid circulation line 4 has a temperature which is not greater than the solidifying point of water by the heat exchange with the liquefied gas in the first heat exchanger 51.
  • the second heat exchanger 52 heat exchange is performed between the working fluid which has passed through the first heat exchanger 51 and is decreased in temperature, and the intermediate heat medium circulating through the intermediate heat medium circulation line 6. Since the intermediate heat medium has a lower solidifying point than water, the intermediate heat medium is hardly solidified during heat exchange with the low-temperature working fluid in the second heat exchanger 52. Thus, it is possible to suppress that the solidified intermediate heat medium freezes to the second heat exchanger 52 and blocks the second heat exchanger 52.
  • the third heat exchanger 53 heat exchange is performed between the heating water and the intermediate heat medium which has passed through the second heat exchanger 52 and is decreased in temperature.
  • the intermediate heat medium is cooled by the heat exchange with the working fluid in the second heat exchanger 52, the temperature higher than the solidifying point of water is maintained even after the cooling.
  • the cold energy recovery system 2 can suppress that the solidified heat medium (the intermediate heat medium, the heating water) freezes to the heat exchanger (the second heat exchanger 52, the third heat exchanger 53) and blocks the heat exchanger, it is possible to improve reliability of the cold energy recovery system 2 when the small heat exchanger is used.
  • the above-described working fluid circulation line 4 includes a bypass flow passage 45 branches from downstream of the second heat exchanger 52, bypasses the turbine 42, and is connected to upstream of the first heat exchanger 51.
  • a flow passage other than the bypass flow passage 45 of the working fluid circulation line 4 described above (a flow passage passing through the turbine 42 or the first heat exchanger 51) will be referred to as a main flow passage 40.
  • the bypass flow passage 45 branches from the main flow passage 40 at a branch portion 451 and joins the main flow passage 40 at a merge portion 452.
  • the above-described cold energy recovery system 2 further includes an on-off valve 46 disposed downstream of the branch portion 451 of the main flow passage 40 and upstream of the turbine 42, and an on-off valve 47 disposed on the bypass flow passage 45.
  • the on-off valve 46 is closed and the on-off valve 47 is opened to allow the working fluid to bypass the turbine 42.
  • the on-off valve 46 is opened and the on-off valve 47 is closed to allow the working flow passage to pass through the turbine 42.
  • the above-described cold energy recovery system 2 is configured to evaporate the intermediate heat medium flowing through the intermediate heat medium circulation line 6 in the third heat exchanger 53, and is configured to condense the intermediate heat medium flowing through the intermediate heat medium circulation line 6 in the second heat exchanger 52. In this case, it is possible to improve the overall efficiency of the cold energy recovery system 2 by utilizing latent heat or sensible heat.
  • the above-described cold energy recovery system 2 further includes the above-described liquefied gas supply line 3, and an auxiliary heat exchanger 81 disposed downstream of the first heat exchanger 51 on the liquefied gas supply line 3.
  • the auxiliary heat exchanger 81 is configured to exchange heat between the liquefied gas flowing downstream of the first heat exchanger 51 through the liquefied gas supply line 3 and a heating medium circulating in the cold energy recovery system 2.
  • the heating medium has a lower solidifying point than water.
  • the auxiliary heat exchanger 81 forms a liquefied gas flow passage 811 which is disposed downstream of the first heat exchanger on the liquefied gas supply line 3 and through which the liquefied gas flows, and a heating medium flow passage 812 through which the heating medium circulating in the cold energy recovery system 2 flows.
  • the heating medium flow passage 812 is disposed at least partially adjacent to the liquefied gas flow passage 811, and heat exchange is performed between the heating medium flowing through the heating medium flow passage 812 and the liquefied gas flow passage 811 flowing through the liquefied gas flow passage 811.
  • the liquefied gas heated by the first heat exchanger 51 is sent to the liquefied gas flow passage 811 of the auxiliary heat exchanger 81.
  • the heat exchange in the auxiliary heat exchanger 81 heats the liquefied gas flowing through the liquefied gas flow passage 811 and cools the heating medium flowing through the heating medium flow passage 812.
  • the heating medium has the lower solidifying point than water, it is possible to suppress solidification during the heat exchange with the liquefied gas in the auxiliary heat exchanger 81.
  • the cold energy recovery system 2 includes the liquefied gas supply line 3, the first heat exchanger 51 disposed on the liquefied gas supply line 3, and the auxiliary heat exchanger 81 disposed downstream of the first heat exchanger 51 on the liquefied gas supply line 3.
  • the heat exchange in the first heat exchanger 51 and the auxiliary heat exchanger 81 raises the temperature of the liquefied gas and vaporizes the liquefied gas. In this case, it is not necessary to raise the temperature to a temperature, at which the liquid liquefied gas is completely vaporized, by the heat exchange in the first heat exchanger 51.
  • the first heat exchanger 51 compared to a case where the temperature of the liquefied gas is raised only by the first heat exchanger 51, it is possible to reduce the amount of the heat exchange in the first heat exchanger 51, and it is possible to reduce the temperature drop of the working fluid in the first heat exchanger 51. Thus, it is possible to effectively suppress solidification of the intermediate heat medium during the heat exchange between the working fluid and the intermediate heat medium in the second heat exchanger 52. Further, by reducing the amount of the heat exchange in the first heat exchanger 51, it is possible to reduce the size of the first heat exchanger 51.
  • the above-described cold energy recovery system 2 is configured such that the above-described liquefied gas supply line 3 does not include a heat exchanger other than the first heat exchanger 51, as shown in FIG. 2 .
  • the liquefied gas is vaporized by the heat exchange in the first heat exchanger 51.
  • the heating medium that exchanges heat with the liquefied gas in the auxiliary heat exchanger 81 described above is constituted by the intermediate heat medium heated by the third heat exchanger 53 and flowing through the intermediate heat medium circulation line 6.
  • the auxiliary heat exchanger 81 heat exchange is performed between the liquefied gas which has passed through the first heat exchanger 51 and is raised in temperature, and the intermediate heat medium heated by the third heat exchanger 53. Since the intermediate heat medium has the lower solidifying point than water, it is possible to suppress solidification during the heat exchange with the liquefied gas in the auxiliary heat exchanger 81. Thus, it is possible to suppress that the solidified intermediate heat medium freezes to the auxiliary heat exchanger 81 and blocks the auxiliary heat exchanger 81. Thus, it is possible to effectively heat the liquefied gas by the auxiliary heat exchanger 81.
  • a circulation pump for circulating the heat medium becomes necessary.
  • the above-described circulation pump becomes unnecessary, making it possible to suppress an equipment cost of the cold energy recovery system 2.
  • the above-described intermediate heat medium circulation line 6 includes a bypass flow passage 63 which branches from downstream of the third heat exchanger 53, bypasses the second heat exchanger 52, and is connected to upstream of the third heat exchanger 53.
  • the above-described auxiliary heat exchanger 81 is configured to exchange heat between the liquefied gas flowing through the liquefied gas supply line 3 and the intermediate heat medium flowing through the bypass flow passage 63.
  • the cold energy recovery system 2 includes: an intermediate heat medium storage device (for example, a buffer tank) 64 which is disposed downstream of the second heat exchanger 52 on the main flow passage 62 and upstream of the intermediate heat medium circulation pump 61, and is configured to store the intermediate heat medium; and a flow regulating valve 65 which is disposed downstream of the auxiliary heat exchanger 81 on the bypass flow passage 63 and is configured to regulate the flow rate of the intermediate heat medium flowing through the bypass flow passage 63.
  • an intermediate heat medium storage device for example, a buffer tank
  • a flow regulating valve 65 which is disposed downstream of the auxiliary heat exchanger 81 on the bypass flow passage 63 and is configured to regulate the flow rate of the intermediate heat medium flowing through the bypass flow passage 63.
  • the bypass flow passage 63 has one end side 631 which is connected to downstream of the third heat exchanger 53 on the main flow passage 62 and upstream of the second heat exchanger 52, and another end side 632 connected to the intermediate heat medium storage device 64.
  • the intermediate heat medium that has passed through the bypass flow passage 63 joins the intermediate heat medium that has passed through the second heat exchanger 52 on the main flow passage 62, in the intermediate heat medium storage device 64.
  • the another end side 632 of the bypass flow passage 63 may be connected to downstream of the second heat exchanger 52 on the main flow passage 62 and upstream of the intermediate heat medium storage device 64.
  • the flow regulating valve 65 is disposed downstream of the auxiliary heat exchanger 81 (more specifically, the heating medium flow passage 812) on the bypass flow passage 63. By regulating the flow rate of the intermediate heat medium flowing through the bypass flow passage 63 with the flow regulating valve 65, the flow rate of the intermediate heat medium passing through the second heat exchanger 52 on the main flow passage 62 is also regulated.
  • the intermediate heat medium is a heat medium responsible for heating in the second heat exchanger 52 and the auxiliary heat exchanger 81
  • the intermediate heat medium is cooled by heat exchange in these heat exchangers.
  • the auxiliary heat exchanger 81 is configured to exchange heat between the liquefied gas and the intermediate heat medium which flows through the bypass flow passage 63 bypassing the second heat exchanger 52. That is, since the intermediate heat medium circulation line 6 does not form the flow passage passing through both the second heat exchanger 52 and the auxiliary heat exchanger 81, it is possible to prevent the temperature of the intermediate heat medium circulating through the intermediate heat medium circulation line 6 from becoming too low. Thus, it is possible to suppress solidification of the heating water during the heat exchange with the intermediate heat medium in the third heat exchanger 53.
  • the above-described cold energy recovery system 2 further includes a second intermediate heat medium circulation line 9 which is configured to circulate a second intermediate heat medium having a lower solidifying point than water.
  • the heating medium which exchanges heat with the liquefied gas in the auxiliary heat exchanger 81 described above is constituted by the second intermediate heat medium flowing through the second intermediate heat medium circulation line 9.
  • the heating medium flow passage 812 of the auxiliary heat exchanger 81 is disposed on the second intermediate heat medium circulation line 9.
  • the cold energy recovery system 2 includes a second intermediate heat medium circulation pump 91 disposed downstream of the auxiliary heat exchanger 81 on the second intermediate heat medium circulation line 9. By driving the circulation pump 91, the second intermediate heat medium circulates through the second intermediate heat medium circulation line 9.
  • the second intermediate heat medium may be the same type of heat medium as the first intermediate heat medium which is the intermediate heat medium flowing through the intermediate heat medium circulation line 6, or may be a different type of heat medium.
  • the second intermediate heat medium is constituted by R1234ZE.
  • the heating medium which exchanges heat with the liquefied gas in the auxiliary heat exchanger 81 is constituted by the second intermediate heat medium flowing through the second intermediate heat medium circulation line 9.
  • the auxiliary heat exchanger 81 heat exchange is performed between the liquefied gas which has passed through the first heat exchanger 51 and is raised in temperature, and the second intermediate heat medium circulating through the second intermediate heat medium circulation line 9. Since the second intermediate heat medium has the lower solidifying point than water, it is possible to suppress solidification during the heat exchange with the liquefied gas in the auxiliary heat exchanger 81. Thus, it is possible to suppress that the solidified second intermediate heat medium freezes to the auxiliary heat exchanger 81 and blocks the auxiliary heat exchanger 81.
  • the second intermediate heat medium circulation line 9 is different from the intermediate heat medium circulation line 6, it is possible to use, as the second intermediate heat medium, a heat medium different from the intermediate heat medium circulating through the intermediate heat medium circulation line 6.
  • the second intermediate heat medium it is possible to use a heat medium which is more suitable for conditions of the heat exchange in the auxiliary heat exchanger 81 than the intermediate heat medium circulating through the intermediate heat medium circulation line 6.
  • the above-described cold energy recovery system 2 further includes a second auxiliary heat exchanger 82 which is configured to exchange heat between the second intermediate heat medium flowing through the second intermediate heat medium circulation line 9 and the heating water introduced from the outside of the cold energy recovery system 2.
  • the second auxiliary heat exchanger 82 forms a second intermediate heat medium flow passage 821 which is disposed downstream of the circulation pump 91 on the second intermediate heat medium circulation line 9 and through which the second intermediate heat medium flows, and a heating water flow passage 822 through which the heating water introduced from the outside of the cold energy recovery system 2 flows.
  • the heating water flow passage 822 is disposed at least partially adjacent to the second intermediate heat medium flow passage 821, and heat exchange is performed between the heating water flowing through the heating water flow passage 822 and the second intermediate heat medium flowing through the second intermediate heat medium flow passage 821.
  • the above-described heating water supply line 7 includes a sub flow passage 72 which branches from downstream of the heating water pump 71 and upstream of the third heat exchanger 53, and is connected to a heating water discharge destination 14B.
  • the heating water flow passage 822 of the second auxiliary heat exchanger 82 is disposed on the sub flow passage 72.
  • a flow passage other than the sub flow passage 72 of the heating water supply line 7 described above (a flow passage passing through the heating water pump 71 or the third heat exchanger 53) will be referred to as a main flow passage 70.
  • the sub flow passage 72 has one end side 721 which is connected to downstream of the heating water pump 71 on the main flow passage 70 and upstream of the third heat exchanger 53, and another end side 722 connected to the heating water discharge destination 14B.
  • a dedicated pump for flowing the heating water to the sub flow passage 72 becomes unnecessary.
  • the another end side 722 of the sub flow passage 72 may be connected to downstream of the third heat exchanger 53 on the main flow passage 70 or the heating water discharge destination 14.
  • the second intermediate heat medium which is boosted by the circulation pump 91 after being cooled by the auxiliary heat exchanger 81, is sent to the second intermediate heat medium flow passage 821. Further, the heating water boosted by the heating water pump 71 is sent to the heating water flow passage 822.
  • the second intermediate heat medium flowing through the second intermediate heat medium flow passage 821 has a higher temperature than the heating water flowing through the heating water flow passage 822.
  • the heat exchange in the second auxiliary heat exchanger 82 heats the second intermediate heat medium flowing through the second intermediate heat medium flow passage 821.
  • the second intermediate heat medium heated by the second auxiliary heat exchanger 82 is sent to the auxiliary heat exchanger 81.
  • the second intermediate heat medium flowing through the second intermediate heat medium flow passage 821 has the temperature higher than the solidifying point of water (heating water).
  • the second intermediate heat medium flowing through the second intermediate heat medium circulation line 9 is cooled by the heat exchange with the liquefied gas in the auxiliary heat exchanger 81, the temperature higher than the solidifying point of water is maintained even after the cooling.
  • the amount of the heat exchange in the auxiliary heat exchanger 81 is small, and the amount of temperature drop of the second intermediate heat medium (heating medium) in the auxiliary heat exchanger 81 is small.
  • the above-described cold energy recovery device 41 includes the above-described turbine 42, and the above-described generator 43 configured to generate electricity by driving the turbine 42.
  • the cold energy recovery device 41 since the cold energy recovery device 41 includes the turbine 42 and the generator 43, it is possible to generate electricity in the generator 43 by driving the turbine 42 with the working fluid which circulates through the working fluid circulation line 4 and recovers the cold energy from the liquefied gas. In this case, it is possible to effectively utilize the cold energy of the liquefied gas.
  • the above-described cold energy recovery system 2 at least includes the liquefied gas supply line 3 configured to send the liquefied gas from the liquefied gas storage device 11, and the liquefied gas pump 31 disposed on the liquefied gas supply line 3.
  • the liquefied gas pump 31 is configured to be driven by the electric power generated by the generator 43.
  • each of the circulation pump 44, the circulation pump 61, the heating water pump 71, and the second intermediate heat medium circulation pump 91 is also configured to be driven by the electric power generated by the generator 43.
  • the circulation pump 44, the circulation pump 61, the heating water pump 71, and the second intermediate heat medium circulation pump 91 may be configured to be driven by the electric power generated by the generator 43.
  • FIG. 6 is an explanatory view for describing an example of the heat exchanger in an embodiment of the present disclosure.
  • the third heat exchanger 53 is constituted by a microchannel heat exchanger 53A.
  • the microchannel heat exchanger 53A includes a first microchannel 531A through which the intermediate heat medium flows, and a second microchannel 532A at least a part of which is disposed adjacent to the first microchannel 531A and through which the heating water flows.
  • the microchannel heat exchanger 53A is constituted by a PCHE (Printed Circuit Heat Exchanger) which is created by alternately stacking and joining to each other first metal plates 533 each in which a plurality of first microchannels 531A are formed and second metal plates 534 each in which a plurality of second microchannels 532A are formed.
  • the microchannel heat exchanger 53A may be a plate heat exchanger or the like.
  • the third heat exchanger 53 is constituted by the microchannel heat exchanger 53A which allows for the heat exchange between the intermediate heat medium flowing through the first microchannels 531A and the heating water flowing through the second microchannels 532A, the third heat exchanger 53 is compact and can improve a heat-transfer coefficient. Since the cold energy recovery system2 using such heat exchanger can reduce the occupied space of the cold energy recovery system 2 in the ship 1, it is possible to increase the occupied space of the liquefied gas storage device 11 in the ship 1.
  • the heat exchanger other than the third heat exchanger 53 may also be the microchannel heat exchanger.
  • the ship 1 includes the above-described cold energy recovery system 2.
  • the small heat exchanger for the heat exchanger of the cold energy recovery system 2 for example, the third heat exchanger 53 or the like
  • it is possible to reduce the occupied space of the cold energy recovery system 2 in the ship 1 it is possible to increase the occupied space of the liquefied gas storage device 11 in the ship 1.
  • FIG. 7 is a flowchart of a cold energy recovery method according to an embodiment of the present disclosure.
  • a cold energy recovery method 100 is a cold energy recovery method by the above-described cold energy recovery system 2 which is installed in the ship 1 including the liquefied gas storage device 11 and as shown in FIG. 7 , at least includes a first heat exchange step S101, a second heat exchange step S102, and a third heat exchange step S103.
  • the first heat exchange step S101 includes performing heat exchange between the liquefied gas and the working fluid by the first heat exchanger 51.
  • the second heat exchange step S102 includes performing, by the second heat exchanger 52, heat exchange between the intermediate heat medium and the working fluid that has exchanged heat with the liquefied gas in the first heat exchange step S101.
  • the third heat exchange step S103 includes performing, by the third heat exchanger 53, heat exchange between the heating water and the intermediate heat medium that has exchanged heat with the working fluid in the second heat exchange step S102.
  • the above method includes the first heat exchange step S101, the second heat exchange step S102, and the third heat exchange step S103.
  • the second heat exchange step S102 and the third heat exchange step S103 cause the heating water and the working fluid circulating through the working fluid circulation line 4 to indirectly exchange heat via the intermediate heat medium circulating through the intermediate heat medium circulation line 6, making it possible to suppress solidification of the heat medium (the intermediate heat medium, the heating water) during the heat exchange.
  • the solidified heat medium freezes to the heat exchanger (the second heat exchanger 52, the third heat exchanger 53) and blocks the heat exchanger.
  • the first heat exchange step S101 includes performing heat exchange between the liquefied gas and the working fluid by the first heat exchanger 51.
  • the working fluid that has passed through the first heat exchanger 51 has a low temperature which is not greater than the solidifying point of water.
  • the second heat exchange step S102 includes performing, by the second heat exchanger 52, heat exchange between the working fluid, which is decreased in temperature by the heat exchange in the first heat exchange step S101, and the intermediate heat medium flowing through the intermediate heat medium circulation line 6. Since the intermediate heat medium has a lower solidifying point than water, the intermediate heat medium is hardly solidified during heat exchange with the low-temperature working fluid in the second heat exchange step S102. Thus, it is possible to suppress that the solidified intermediate heat medium freezes to the second heat exchanger 52 and blocks the second heat exchanger 52.
  • the third heat exchange step S103 includes performing, by the third heat exchanger 53, heat exchange between the heating water and the intermediate heat medium which is decreased in temperature by the heat exchange in the second heat exchange step S102.
  • the intermediate heat medium is cooled by the heat exchange with the working fluid in the second heat exchange step S102, the temperature higher than the solidifying point of water is maintained even after the cooling.
  • the solidified heat medium (the intermediate heat medium, the heating water) freezes to the heat exchanger (the second heat exchanger 52, the third heat exchanger 53) and blocks the heat exchanger, it is possible to improve reliability of the cold energy recovery system 2 when the small heat exchanger is used.
  • the cold energy recovery method 100 may further include a first auxiliary heat exchange step S201 or a second auxiliary heat exchange step S202.
  • the first auxiliary heat exchange step S201 includes performing, by the auxiliary heat exchanger 81, heat exchange between the above-described heating water and the liquefied gas which is raised in temperature by the heat exchange in the first heat exchange step S101.
  • the second auxiliary heat exchange step S202 includes performing, by the second auxiliary heat exchanger 82, heat exchange between the heating water and the second intermediate heat medium flowing through the second intermediate heat medium circulation line 9.
  • the present invention is not limited to the above-described embodiments, and also includes an embodiment obtained by modifying the above-described embodiments and an embodiment obtained by combining these embodiments as appropriate, within the scope of the appended claims.
  • a cold energy recovery system (2) is a cold energy recovery system (2) installed in a ship (1) which includes a liquefied gas storage device (11) configured to store a liquid liquefied gas, that includes a working fluid circulation line (4) which is configured to circulate a working fluid having a lower solidifying point than water, a cold energy recovery device (41) that includes a turbine (42) which is configured to be driven by the working fluid flowing through the working fluid circulation line (4), a first heat exchanger (51) which is configured to exchange heat between the liquefied gas and the working fluid flowing through the working fluid circulation line (4), an intermediate heat medium circulation line (6) which is configured to circulate an intermediate heat medium having a lower solidifying point than water, a second heat exchanger (52) disposed downstream of the first heat exchanger (51) on the working fluid circulation line (4), the second heat exchanger (52) being configured to exchange heat between the working fluid flowing through the working fluid circulation line (4) and the intermediate heat medium flowing through the intermediate heat medium circulation line (6), and a third heat exchanger (53) which is configured
  • the cold energy recovery system (2) includes the intermediate heat medium circulation line (6), the second heat exchanger (52), and the third heat exchanger (53).
  • the heating water and the working fluid circulating through the working fluid circulation line (4) indirectly exchange heat via the intermediate heat medium circulating through the intermediate heat medium circulation line (6), making it possible to suppress solidification of the heat medium (the intermediate heat medium, the heating water) during heat exchange.
  • the solidified heat medium freezes to the heat exchanger (the second heat exchanger 52, the third heat exchanger 53) and blocks the heat exchanger.
  • the working fluid circulating through the working fluid circulation line (4) has a temperature which is not greater than the solidifying point of water by the heat exchange with the liquefied gas in the first heat exchanger (51).
  • heat exchange is performed between the working fluid which has passed through the first heat exchanger (51) and is decreased in temperature, and the intermediate heat medium circulating through the intermediate heat medium circulation line (6). Since the intermediate heat medium has a lower solidifying point than water, the intermediate heat medium is hardly solidified during heat exchange with the low-temperature working fluid in the second heat exchanger (52). Thus, it is possible to suppress that the solidified intermediate heat medium freezes to the second heat exchanger (52) and blocks the second heat exchanger (52).
  • the third heat exchanger (53) heat exchange is performed between the heating water and the intermediate heat medium which has passed through the second heat exchanger (51) and is decreased in temperature.
  • the intermediate heat medium is cooled by the heat exchange with the working fluid in the second heat exchanger (51), the temperature higher than the solidifying point of water is maintained even after the cooling.
  • the cold energy recovery system (2) can suppress that the solidified heat medium (the intermediate heat medium, the heating water) freezes to the heat exchanger (the second heat exchanger 52, the third heat exchanger 53) and blocks the heat exchanger, it is possible to improve reliability of the cold energy recovery system (2) when the small heat exchanger is used.
  • the cold energy recovery system (2) further includes a liquefied gas supply line (3) configured to send the liquefied gas from the liquefied gas storage device (11), and an auxiliary heat exchanger (81) disposed downstream of the first heat exchanger (51) on the liquefied gas supply line (3), the auxiliary heat exchanger (81) being configured to exchange heat between the liquefied gas flowing through the liquefied gas supply line (3) and a heating medium circulating in the cold energy recovery system (2).
  • the cold energy recovery system (2) includes the liquefied gas supply line (3), the above-described first heat exchanger (51), and the auxiliary heat exchanger (81).
  • the heat exchange in the first heat exchanger (51) and the auxiliary heat exchanger (81) raises the temperature of the liquefied gas and vaporizes the liquefied gas. In this case, it is not necessary to raise the temperature to a temperature, at which the liquid liquefied gas is completely vaporized, by the heat exchange in the first heat exchanger (51).
  • the first heat exchanger (51) compared to a case where the temperature of the liquefied gas is raised only by the first heat exchanger (51), it is possible to reduce the amount of the heat exchange in the first heat exchanger (51), and it is possible to reduce the temperature drop of the working fluid in the first heat exchanger (51). Thus, it is possible to effectively suppress solidification of the intermediate heat medium during the heat exchange between the working fluid and the intermediate heat medium in the second heat exchanger (52). Further, by reducing the amount of the heat exchange in the first heat exchanger (51), it is possible to reduce the size of the first heat exchanger (51).
  • the heating medium is constituted by the intermediate heat medium heated by the third heat exchanger (53) and flowing through the intermediate heat medium circulation line (6).
  • the auxiliary heat exchanger (81) heat exchange is performed between the liquefied gas which has passed through the first heat exchanger (51) and is raised in temperature, and the intermediate heat medium heated by the third heat exchanger (53). Since the intermediate heat medium has the lower solidifying point than water, it is possible to suppress solidification during the heat exchange with the liquefied gas in the auxiliary heat exchanger (81). Thus, it is possible to suppress that the solidified intermediate heat medium freezes to the auxiliary heat exchanger (81) and blocks the auxiliary heat exchanger (81). Thus, it is possible to effectively heat the liquefied gas by the auxiliary heat exchanger (81).
  • a circulation pump for circulating the heat medium becomes necessary.
  • the above-described circulation pump becomes unnecessary, making it possible to suppress an equipment cost of the cold energy recovery system (2).
  • the intermediate heat medium circulation line (6) may include a bypass flow passage (63) which branches from downstream of the third heat exchanger (53), bypasses the second heat exchanger (52), and is connected to upstream of the third heat exchanger (53), and the auxiliary heat exchanger (81) is configured to exchange heat between the liquefied gas flowing through the liquefied gas supply line (3) and the intermediate heat medium flowing through the bypass flow passage (63).
  • the intermediate heat medium is a heat medium responsible for heating in the second heat exchanger (52) and the auxiliary heat exchanger (81), the intermediate heat medium is cooled by heat exchange in these heat exchangers.
  • the auxiliary heat exchanger (81) is configured to exchange heat between the liquefied gas and the intermediate heat medium which flows through the bypass flow passage (63) bypassing the second heat exchanger (52). That is, since the intermediate heat medium circulation line (6) does not form the flow passage passing through both the second heat exchanger (52) and the auxiliary heat exchanger (81), it is possible to prevent the temperature of the intermediate heat medium circulating through the intermediate heat medium circulation line (6) from becoming too low. Thus, it is possible to suppress solidification of the heating water during the heat exchange with the intermediate heat medium in the third heat exchanger (53).
  • the cold energy recovery system (2) may further include a second intermediate heat medium circulation line (9) which is configured to circulate a second intermediate heat medium having a lower solidifying point than water.
  • the heating medium is constituted by the second intermediate heat medium flowing through the second intermediate heat medium circulation line (9).
  • the heating medium which exchanges heat with the liquefied gas in the auxiliary heat exchanger (81) is constituted by the second intermediate heat medium flowing through the second intermediate heat medium circulation line (9).
  • the auxiliary heat exchanger (81) heat exchange is performed between the liquefied gas which has passed through the first heat exchanger (51) and is raised in temperature, and the second intermediate heat medium circulating through the second intermediate heat medium circulation line (9). Since the second intermediate heat medium has the lower solidifying point than water, it is possible to suppress solidification during the heat exchange with the liquefied gas in the auxiliary heat exchanger (81). Thus, it is possible to suppress that the solidified second intermediate heat medium freezes to the auxiliary heat exchanger (81) and blocks the auxiliary heat exchanger (81).
  • the second intermediate heat medium circulation line (9) is different from the intermediate heat medium circulation line (6), it is possible to use, as the second intermediate heat medium, a heat medium different from the intermediate heat medium circulating through the intermediate heat medium circulation line (6).
  • the second intermediate heat medium it is possible to use a heat medium which is more suitable for conditions of the heat exchange in the auxiliary heat exchanger (81) than the intermediate heat medium circulating through the intermediate heat medium circulation line (6).
  • the cold energy recovery system (2) may further include a second auxiliary heat exchanger (82) which is configured to exchange heat between the second intermediate heat medium flowing through the second intermediate heat medium circulation line (9) and heating water introduced from an outside of the cold energy recovery system (2).
  • a second auxiliary heat exchanger (82) which is configured to exchange heat between the second intermediate heat medium flowing through the second intermediate heat medium circulation line (9) and heating water introduced from an outside of the cold energy recovery system (2).
  • the heat exchange in the first heat exchanger (51) and the auxiliary heat exchanger (81) raises the temperature of the liquefied gas, the amount of the heat exchange in the auxiliary heat exchanger (81) is small, and the amount of temperature drop of the second intermediate heat medium (heating medium) in the auxiliary heat exchanger (81) is small.
  • the cold energy recovery device (41) may further include a generator (43) configured to generate electricity by driving the turbine (42).
  • the cold energy recovery device (41) includes the turbine (42) and the generator (43), it is possible to generate electricity in the generator (43) by driving the turbine (42) with the working fluid which circulates through the working fluid circulation line 4 and recovers the cold energy from the liquefied gas. In this case, it is possible to effectively utilize the cold energy of the liquefied gas.
  • the cold energy recovery system (2) may further include a liquefied gas supply line (3) configured to send the liquefied gas from the liquefied gas storage device (11), and a liquefied gas pump (31) disposed on the liquefied gas supply line (3).
  • the liquefied gas pump (31) is configured to be driven by electric power generated by the generator (43).
  • the third heat exchanger (53) may be constituted by a microchannel heat exchanger (53A) that includes a first microchannel (531A) through which the intermediate heat medium flows, and a second microchannel (532A) through which the heating water flows, at least a part of the second microchannel (532A) being disposed adjacent to the first microchannel (531A).
  • the third heat exchanger (53) is constituted by the microchannel heat exchanger (53A) which allows for the heat exchange between the intermediate heat medium flowing through the first microchannel (531A) and the heating water flowing through the second microchannel (532A), the third heat exchanger (53) is compact and can improve a heat-transfer coefficient.
  • a ship (1) includes the above described cold energy recovery system (2) , since it is possible to reduce the size of the cold energy recovery system (2) by using the small heat exchanger, it is possible to reduce the size of the ship (1) having the cold energy recovery system (2).
  • a cold energy recovery method (100) is a cold energy recovery method (100) by a cold energy recovery system (2) installed in a ship (1) which includes a liquefied gas storage device (11) configured to store a liquid liquefied gas, the cold energy recovery system (2) including a working fluid circulation line (4) which is configured to circulate a working fluid having a lower solidifying point than water, a cold energy recovery device (41) that includes a turbine (42) which is configured to be driven by the working fluid flowing through the working fluid circulation line (4), a first heat exchanger (51) which is configured to exchange heat between the liquefied gas and the working fluid flowing through the working fluid circulation line (4), an intermediate heat medium circulation line (6) which is configured to circulate an intermediate heat medium having a lower solidifying point than water, a second heat exchanger (52) disposed downstream of the first heat exchanger (51) on the working fluid circulation line (4), the second heat exchanger (52) being configured to exchange heat between the working fluid flowing through the working fluid circulation line (4) and the intermediate heat medium flowing through the intermediate heat medium
  • the above method includes the first heat exchange step (S101), the second heat exchange step (S102), and the third heat exchange step (S103).
  • the second heat exchange step (S102) and the third heat exchange step (S103) cause the heating water and the working fluid circulating through the working fluid circulation line (4) to indirectly exchange heat via the intermediate heat medium circulating through the intermediate heat medium circulation line (6), making it possible to suppress solidification of the heat medium (the intermediate heat medium, the heating water) during heat exchange.
  • the solidified heat medium freezes to the heat exchanger (the second heat exchanger 52, the third heat exchanger 53) and blocks the heat exchanger.
  • the first heat exchange step (S101) includes performing heat exchange between the liquefied gas and the working fluid by the first heat exchanger (51).
  • the working fluid that has passed through the first heat exchanger (51) has a low temperature which is not greater than the solidifying point of water.
  • the second heat exchange step (S102) includes performing, by the second heat exchanger (52), heat exchange between the working fluid, which is decreased in temperature by the heat exchange in the first heat exchange step (S101), and the intermediate heat medium flowing through the intermediate heat medium circulation line (6). Since the intermediate heat medium has a lower solidifying point than water, the intermediate heat medium is hardly solidified during heat exchange with the low-temperature working fluid in the second heat exchange step. Thus, it is possible to suppress that the solidified intermediate heat medium freezes to the second heat exchanger (52) and blocks the second heat exchanger (52).
  • the third heat exchange step (S103) includes performing, by the third heat exchanger (53), heat exchange between the heating water and the intermediate heat medium which is decreased in temperature by the heat exchange in the second heat exchange step (S102).
  • the intermediate heat medium is cooled by the heat exchange with the working fluid in the second heat exchange step (S102)
  • the temperature higher than the solidifying point of water is maintained even after the cooling.

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Claims (8)

  1. In einem Schiff (1) installiertes Kälteenergierückgewinnungssystem (2), das eine Flüssiggas-Speichervorrichtung (11) einschließt, die zum Speichern von flüssigem Flüssiggas konfiguriert ist, umfassend:
    eine Arbeitsfluid-Zirkulationsleitung (4), die so konfiguriert ist, dass sie ein Arbeitsfluid zirkulieren lässt, das einen niedrigeren Erstarrungspunkt als Wasser aufweist;
    eine Kälteenergierückgewinnungsvorrichtung (41), die eine Turbine (42) einschließt, die so konfiguriert ist, dass sie durch das Arbeitsfluid angetrieben wird, das durch die Arbeitsfluid-Zirkulationsleitung (4) fließt;
    einen ersten Wärmetauscher (51), der so konfiguriert ist, dass er Wärme zwischen dem verflüssigten Gas und dem durch die Arbeitsfluid-Zirkulationsleitung (4) fließenden Arbeitsfluid austauscht;
    eine Zwischenwärmemedium-Zirkulationsleitung (6), die so konfiguriert ist, dass sie ein Zwischenwärmemedium zirkulieren lässt, das einen niedrigeren Erstarrungspunkt als Wasser aufweist;
    einen zweiten Wärmetauscher (52), der stromabwärts vom ersten Wärmetauscher (51) in der Arbeitsfluid-Zirkulationsleitung (4) angeordnet ist, wobei der zweite Wärmetauscher (52) so konfiguriert ist, dass er Wärme zwischen dem durch die Arbeitsfluid-Zirkulationsleitung (4) fließenden Arbeitsfluid und dem durch die Zwischenwärmemedium-Zirkulationsleitung (6) fließenden Zwischenwärmemedium austauscht;
    einen dritten Wärmetauscher (53), der so konfiguriert ist, dass er Wärme zwischen dem durch die Zwischenwärmemedium-Zirkulationsleitung (6) fließenden Zwischenwärmemedium und dem von außerhalb des Kälteenergierückgewinnungssystems (2) zugeführten Heizwasser austauscht;
    eine Flüssiggasversorgungsleitung (3), die so konfiguriert ist, dass sie das Flüssiggas aus der Flüssiggas-Speichervorrichtung (11) schickt; und
    einen Hilfswärmetauscher (81), der stromabwärts des ersten Wärmetauschers (51) an der Flüssiggasversorgungsleitung (3) angeordnet ist, wobei der Hilfswärmetauscher (81) so konfiguriert ist, dass er Wärme zwischen dem durch die Flüssiggasversorgungsleitung (3) fließenden Flüssiggas und einem im Kälteenergierückgewinnungssystem (2) zirkulierenden Heizmedium austauscht,
    wobei das Heizmedium aus dem durch den dritten Wärmetauscher (53) erhitzten Zwischenwärmemedium besteht und durch die Zwischenwärmemedium-Zirkulationsleitung (6) fließt.
  2. Kälteenergierückgewinnungssystem (2) nach Anspruch 1,
    wobei die Zwischenwärmemedium-Zirkulationsleitung (6) eine Umgehungspassage (63) einschließt, die stromabwärts des dritten Wärmetauschers (53) abzweigt, den zweiten Wärmetauscher (52) umgeht und stromaufwärts des dritten Wärmetauschers (53) verbunden ist, und
    wobei der Hilfswärmetauscher (81) so konfiguriert ist, dass er Wärme zwischen dem durch die Flüssiggasversorgungsleitung (3) fließenden Flüssiggas und dem durch die Umgehungspassage (63) fließenden Zwischenwärmemedium austauscht.
  3. Kälteenergierückgewinnungssystem (2) nach Anspruch 1,
    weiter umfassend eine zweite Zwischenwärmemedium-Zirkulationsleitung (9), die so konfiguriert ist, dass sie ein zweites Zwischenwärmemedium zirkulieren lässt, das einen niedrigeren Erstarrungspunkt als Wasser aufweist,
    wobei das Heizmedium aus dem zweiten Zwischenwärmemedium besteht, das durch die zweite Zwischenwärmemedium-Zirkulationsleitung (9) fließt.
  4. Kälteenergierückgewinnungssystem (2) nach Anspruch 3, weiter umfassend einen zweiten Hilfswärmetauscher (82), der so konfiguriert ist, dass er Wärme zwischen dem zweiten Zwischenwärmemedium, das durch die zweite Zwischenwärmemedium-Zirkulationsleitung (9) fließt, und Heizwasser, das von außerhalb des Kälteenergierückgewinnungssystems (2) zugeführt wird, austauscht.
  5. Kälteenergierückgewinnungssystem (2) nach einem der Ansprüche 1 bis 4,
    wobei die Kälteenergierückgewinnungsvorrichtung (41) weiter einen Generator (43) einschließt, der so konfiguriert ist, dass er durch Antreiben der Turbine (42) Elektrizität erzeugt.
  6. Kälteenergierückgewinnungssystem (2) nach Anspruch 5, weiter umfassend:
    eine Flüssiggas-Versorgungsleitung (3), die so konfiguriert ist, dass sie das Flüssiggas aus der Flüssiggas-Speichervorrichtung (11) schickt; und
    eine Flüssiggas-Pumpe (31), die an der Flüssiggas-Versorgungsleitung (3) angeordnet ist,
    wobei die Flüssiggas-Pumpe (31) so konfiguriert ist, dass sie durch elektrische Energie angetrieben wird, die vom Generator (43) erzeugt wird.
  7. Kälteenergierückgewinnungssystem (2) nach einem der Ansprüche 1 bis 6,
    wobei der dritte Wärmetauscher (53) aus einem Mikrokanal-Wärmetauscher (53A) besteht, der Folgendes einschließt:
    einen ersten Mikrokanal (531A), durch den das Zwischenwärmemedium fließt; und
    einen zweiten Mikrokanal (532A), durch den das Heizwasser fließt, wobei zumindest ein Teil des zweiten Mikrokanals (532A) benachbart zum ersten Mikrokanal (531A) angeordnet ist.
  8. Verfahren (100) zur Rückgewinnung von Kälteenergie durch ein Kälteenergierückgewinnungssystem (2), das in einem Schiff (1) installiert ist und eine Flüssiggas-Speichervorrichtung (11) einschließt, die zum Speichern von flüssigem Flüssiggas konfiguriert ist,
    wobei die Kälteenergierückgewinnungssystem (2) Folgendes einschließt:
    eine Arbeitsfluid-Zirkulationsleitung (4), die so konfiguriert ist, dass sie ein Arbeitsfluid zirkulieren lässt, das einen niedrigeren Erstarrungspunkt als Wasser aufweist;
    eine Kälteenergierückgewinnungsvorrichtung (41), die eine Turbine (42) einschließt, die so konfiguriert ist, dass sie durch das Arbeitsfluid angetrieben wird, das durch die Arbeitsfluid-Zirkulationsleitung (4) fließt;
    einen ersten Wärmetauscher (51), der so konfiguriert ist, dass er Wärme zwischen dem verflüssigten Gas und dem durch die Arbeitsfluid-Zirkulationsleitung (4) fließenden Arbeitsfluid austauscht;
    eine Zwischenwärmemedium-Zirkulationsleitung (6), die so konfiguriert ist, dass sie ein Zwischenwärmemedium zirkulieren lässt, das einen niedrigeren Erstarrungspunkt als Wasser aufweist;
    einen zweiten Wärmetauscher (52), der stromabwärts vom ersten Wärmetauscher (51) in der Arbeitsfluid-Zirkulationsleitung (4) angeordnet ist, wobei der zweite Wärmetauscher (52) so konfiguriert ist, dass er Wärme zwischen dem durch die Arbeitsfluid-Zirkulationsleitung (4) fließenden Arbeitsfluid und dem durch die Zwischenwärmemedium-Zirkulationsleitung (6) fließenden Zwischenwärmemedium austauscht;
    einen dritten Wärmetauscher (53), der so konfiguriert ist, dass er Wärme zwischen dem durch die Zwischenwärmemedium-Zirkulationsleitung (6) fließenden Zwischenwärmemedium und dem von außerhalb des Kälteenergierückgewinnungssystems (2) zugeführten Heizwasser austauscht;
    eine Flüssiggas-Versorgungsleitung (3), die so konfiguriert ist, dass sie das Flüssiggas aus der Flüssiggas-Speichervorrichtung (11) schickt; und
    einen Hilfswärmetauscher (81), der stromabwärts des ersten Wärmetauschers (51) an der Flüssiggasversorgungsleitung (3) angeordnet ist, wobei der Hilfswärmetauscher (81) so konfiguriert ist, dass er Wärme zwischen dem durch die Flüssiggasversorgungsleitung (3) fließenden Flüssiggas und einem im Kälteenergierückgewinnungssystem (2) zirkulierenden Heizmedium austauscht,
    wobei das Heizmedium aus dem durch den dritten Wärmetauscher (53) erhitzten Zwischenwärmemedium besteht, das durch die Zwischenwärmemedium-Zirkulationsleitung (6) fließt, und
    wobei das Verfahren zur Rückgewinnung von Kälteenergie Folgendes umfasst:
    einen ersten Wärmeaustauschschritt (S101) zum Durchführen eines Wärmeaustauschs zwischen dem verflüssigten Gas und dem Arbeitsfluid durch den ersten Wärmetauscher (51);
    einen zweiten Wärmeaustauschschritt (S102), bei dem durch den zweiten Wärmetauscher (52) ein Wärmeaustausch zwischen dem Zwischenwärmemedium und dem Arbeitsfluid durchgeführt wird, das im ersten Wärmeaustauschschritt (S101) Wärme mit dem verflüssigten Gas ausgetauscht hat; und
    einen dritten Wärmeaustauschschritt (S103), bei dem durch den dritten Wärmetauscher (53) ein Wärmeaustausch zwischen dem Heizwasser und dem Zwischenwärmemedium durchgeführt wird, das im zweiten Wärmeaustauschschritt (S102) Wärme mit dem Arbeitsfluid ausgetauscht hat.
EP20893934.8A 2019-11-26 2020-11-26 Kälterückgewinnungssystem, schiff mit kälterückgewinnungssystem und kälterückgewinnungsverfahren Active EP4035985B1 (de)

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PCT/JP2020/043956 WO2021106984A1 (ja) 2019-11-26 2020-11-26 冷熱回収システム、冷熱回収システムを備える船舶、および冷熱回収方法

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EP4035985A1 (de) 2022-08-03
CN114651148A (zh) 2022-06-21
KR20220062651A (ko) 2022-05-17
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WO2021106984A1 (ja) 2021-06-03
JP7288842B2 (ja) 2023-06-08

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