WO2017104698A1 - 船舶 - Google Patents
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- WO2017104698A1 WO2017104698A1 PCT/JP2016/087197 JP2016087197W WO2017104698A1 WO 2017104698 A1 WO2017104698 A1 WO 2017104698A1 JP 2016087197 W JP2016087197 W JP 2016087197W WO 2017104698 A1 WO2017104698 A1 WO 2017104698A1
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- WIPO (PCT)
- Prior art keywords
- gas
- pressure
- boil
- return
- supply line
- Prior art date
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Classifications
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- 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
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H21/00—Use of propulsion power plant or units on vessels
- B63H21/12—Use of propulsion power plant or units on vessels the vessels being motor-driven
- B63H21/14—Use of propulsion power plant or units on vessels the vessels being motor-driven relating to internal-combustion engines
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B63—SHIPS OR OTHER WATERBORNE VESSELS; RELATED EQUIPMENT
- B63H—MARINE PROPULSION OR STEERING
- B63H21/00—Use of propulsion power plant or units on vessels
- B63H21/38—Apparatus or methods specially adapted for use on marine vessels, for handling power plant or unit liquids, e.g. lubricants, coolants, fuels or the like
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B43/00—Engines characterised by operating on gaseous fuels; Plants including such engines
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
- F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
- F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
- F02M21/0203—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels characterised by the type of gaseous fuel
- F02M21/0209—Hydrocarbon fuels, e.g. methane or acetylene
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M21/00—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form
- F02M21/02—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels
- F02M21/0203—Apparatus for supplying engines with non-liquid fuels, e.g. gaseous fuels stored in liquid form for gaseous fuels characterised by the type of gaseous fuel
- F02M21/0215—Mixtures of gaseous fuels; Natural gas; Biogas; Mine gas; Landfill gas
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M25/00—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture
- F02M25/08—Engine-pertinent apparatus for adding non-fuel substances or small quantities of secondary fuel to combustion-air, main fuel or fuel-air mixture adding fuel vapours drawn from engine fuel reservoir
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- 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
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- 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
- F17C13/004—Details of vessels or of the filling or discharging of vessels for large storage vessels not under pressure
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- 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
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
- F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
- F17C2227/00—Transfer of fluids, i.e. method or means for transferring the fluid; Heat exchange with the fluid
- F17C2227/03—Heat exchange with the fluid
- F17C2227/0337—Heat exchange with the fluid by cooling
- F17C2227/0339—Heat exchange with the fluid by cooling using the same fluid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F17—STORING OR DISTRIBUTING GASES OR LIQUIDS
- F17C—VESSELS FOR CONTAINING OR STORING COMPRESSED, LIQUEFIED OR SOLIDIFIED GASES; FIXED-CAPACITY GAS-HOLDERS; FILLING VESSELS WITH, OR DISCHARGING FROM VESSELS, COMPRESSED, LIQUEFIED, OR SOLIDIFIED GASES
- F17C2265/00—Effects achieved by gas storage or gas handling
- F17C2265/03—Treating the boil-off
- F17C2265/031—Treating the boil-off by discharge
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- 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
- 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
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/30—Use of alternative fuels, e.g. biofuels
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T70/00—Maritime or waterways transport
- Y02T70/50—Measures to reduce greenhouse gas emissions related to the propulsion system
- Y02T70/5218—Less carbon-intensive fuels, e.g. natural gas, biofuels
Definitions
- the present invention relates to a ship including a gas engine.
- a ship including a tank for storing liquefied natural gas and a propulsion gas engine in which boil-off gas generated in the tank is supplied as fuel gas is known.
- the boil-off gas is supplied to the gas engine after being boosted to a pressure range required by the gas engine by the compressor.
- the surplus gas is returned to the tank or incinerated with a gas combustion device or the like. ing.
- Patent Document 1 discloses a ship 100 that boosts boil-off gas introduced from a tank 110 with a high-pressure gas compressor 120 and supplies the boosted gas to a gas-fired engine.
- the ship 100 includes a return line 130 that partially liquefies the gas compressed by the high-pressure gas compressor 120 and returns it to the liquefied natural gas in the tank 110.
- a flow rate control valve 131, a heat exchanger 132, an expansion valve 133, and a gas-liquid separator 134 are provided in this order from the upstream side.
- the flow rate control valve 131 adjusts the flow rate of the boil-off gas transferred to the heat exchanger 132 according to the ship speed.
- the boil-off gas compressed by the high-pressure gas compressor 120 passes through the flow control valve 131, is cooled by the heat exchanger 132, is at least partially liquefied, and is expanded by the expansion valve 133.
- the boil-off gas that has become low pressure and low temperature by being expanded is separated into a gas component and a liquid component by the gas-liquid separator 134, and only the liquid component is returned to the tank 110 by the transfer pump 135.
- the gas component merges with the boil-off gas that is led from the tank 110 to the high-pressure gas compressor 120 through the recirculation line 137 provided with the pressure regulating valve 136 from the gas-liquid separator 134.
- the downstream end of the recirculation line 137 is connected to a line that leads from the tank 110 to the high-pressure gas compressor 120.
- the boil-off gas in the tank 110 is consequently obtained.
- the reliquefaction rate of the boil-off gas flowing through the return line 130 ratio of the reliquefaction amount with respect to the boil-off gas return amount
- an object of the present invention is to provide a ship that can improve the reliquefaction rate of boil-off gas returned to the tank through the return line.
- the inventors of the present application have conducted intensive research and optimized the pressure of the boil-off gas upstream of the expansion device such as the expansion valve to thereby reduce the boil-off gas after passing through the expansion device. It has been found that the reliquefaction rate is improved.
- the present invention has been made from such a viewpoint.
- the ship of the present invention includes a gas engine, a tank for storing liquefied natural gas, a supply line provided with a compressor for guiding boil-off gas generated in the tank to the gas engine as fuel gas, A return line provided with an expansion device branched from the supply line downstream of the compressor and connected to the tank, and an opening degree change provided in an upstream portion of the return line from the expansion device.
- a return valve, a heat exchanger for exchanging heat between the boil-off gas flowing between the return valve and the expansion device in the return line and the heat medium, and the return valve and the expansion device in the return line A pressure gauge for detecting the pressure of the boil-off gas flowing between the pressure gauge and the return pressure so that the pressure of the boil-off gas detected by the pressure gauge becomes a set pressure. And a control device for controlling the valve.
- the control device controls the return valve so that the pressure of the boil-off gas flowing between the return valve and the expansion device in the return line becomes the set pressure, the boil-off after passing through the expansion device The reliquefaction rate of gas can be improved.
- the pressure gauge is a first pressure gauge
- the ship further includes a second pressure gauge that detects a pressure of boil-off gas that flows in a portion downstream of the compressor in the supply line
- the control device may increase the opening of the return valve in preference to the control based on the set pressure when the pressure of the boil-off gas detected by the second pressure gauge exceeds a threshold value.
- the heat exchanger is between a boil-off gas that flows between the return valve and the expansion device in the return line and a boil-off gas that flows in an upstream portion of the compressor in the supply line. Heat exchange may be performed. According to this configuration, the boil-off gas flowing in the return line can be cooled using the boil-off gas flowing in the upstream portion of the supply line from the compressor.
- the gas engine is a main gas engine
- the supply line is a first supply line
- the ship takes out a liquefied natural gas from a sub-gas engine for power generation and the tank
- a second supply line that guides the vaporized gas obtained by vaporizing the liquefied natural gas to the auxiliary gas engine as a fuel gas
- the heat exchanger flows between the return valve and the expansion device in the return line. Heat exchange may be performed between the boil-off gas and the liquefied natural gas flowing through the second supply line. According to this configuration, the boil-off gas flowing through the return line can be cooled using the liquefied natural gas flowing through the second supply line.
- the reliquefaction rate of the boil-off gas returned to the tank through the return line can be improved.
- 1 is a schematic configuration diagram of a ship according to a first embodiment. It is a Mollier diagram of boil-off gas which flows into the 1st supply line and return line in a 1st embodiment. It is a schematic block diagram of the ship which concerns on 2nd Embodiment. It is a schematic block diagram of the conventional ship.
- FIG. 1 shows a ship 1A according to the first embodiment of the present invention.
- the ship 1A includes a tank 11 that stores liquefied natural gas (hereinafter referred to as LNG), a main gas engine 12 for propulsion, and a sub gas engine 13 for power generation (that is, for inboard power).
- LNG liquefied natural gas
- main gas engine 12 for propulsion liquefied natural gas
- sub gas engine 13 for power generation that is, for inboard power
- only one tank 11 is provided, but a plurality of tanks 11 may be provided.
- the vessel 1A is an LNG carrier, the vessel 1A is equipped with a plurality of tanks 11 as cargo tanks.
- one main gas engine 12 and one sub gas engine 13 are provided, but a plurality of main gas engines 12 may be provided, or a plurality of sub gas engines 13 may be provided. Good.
- the ship 1A is a mechanical propulsion type, and the main gas engine 12 directly rotates and drives a screw propeller (not shown).
- the ship 1A may be an electric propulsion type, and the main gas engine 12 may rotationally drive the screw propeller via an electric motor.
- the main gas engine 12 is a diesel cycle type two-stroke engine having a high fuel gas injection pressure of about 20 to 35 MPa, for example.
- the main gas engine 12 may be an Otto cycle type two-stroke engine having a medium pressure of, for example, a fuel gas injection pressure of about 1 to 2 MPa.
- the main gas engine 12 may be an Otto cycle type four-stroke engine having a low fuel gas injection pressure of, for example, about 0.5 to 1 MPa.
- the main gas engine 12 may be a gas-only combustion engine that burns only fuel gas, or may be a dual fuel engine that burns one or both of fuel gas and fuel oil (binary fuel engine). In this case, the fuel gas may be burned by the Otto cycle, and the fuel oil may be burned by the diesel cycle).
- the auxiliary gas engine 13 is an Otto cycle type four-stroke engine having a low fuel gas injection pressure of about 0.5 to 1 MPa, for example, and is connected to a generator (not shown).
- the auxiliary gas engine 13 may be a gas-only engine that burns only fuel gas, or may be a dual fuel engine that burns one or both of fuel gas and fuel oil.
- Boil-off gas (hereinafter referred to as BOG) generated in the tank 11 by natural heat input is led to the main gas engine 12 as the main fuel gas by the first supply line 14.
- a gas obtained by vaporizing LNG taken out from the tank 11 (hereinafter referred to as VG) is led to the auxiliary gas engine 13 as a main fuel gas by the second supply line 15.
- the first supply line 14 is provided with a compressor 16 that compresses the BOG guided from the tank 11 to a high pressure.
- the compressor 16 is a multistage high-pressure compressor that compresses the guided BOG in stages.
- the compressor 16 may be a low-pressure compressor, for example, when the fuel gas injection pressure of the main gas engine 12 is low.
- the compressor 16 compresses the BOG to the supercritical state, in other words, to a pressure higher than the supercritical pressure Pc (intersection of the saturated liquid line L1 and the saturated vapor line L2) in FIG.
- the pressure of BOG discharged from the compressor 16 is about 20 to 35 MPa, and the temperature is about 45 to 55 ° C.
- the return line 2 branches off from the downstream side portion 14b of the compressor 16 in the first supply line 14.
- the return line 2 extends from the branch point 14 c of the first supply line 14 and is connected to the tank 11.
- the tip of the return line 2 may be located above the liquid level of LNG in the tank 11 or may be located below the liquid level.
- the return line 2 is provided with a return valve 21, a heat exchanger 22, and an expansion device 23 in order from the upstream side.
- the return valve 21 is a pressure control valve whose opening degree can be changed.
- the return valve 21 may be a flow rate control valve instead of the pressure control valve.
- the return valve 21 depressurizes BOG returned to the tank 11 through the return line 2.
- the BOG decompressed by the return valve 21 flows into the heat exchanger 22.
- BOG is returned through the return line 2 by opening and closing the return valve 21, but an opening / closing valve may be provided in the return line 2 separately from the return valve 21.
- the heat exchanger 22 exchanges heat between the BOG that flows in the upstream portion 14a of the compressor 16 in the first supply line 14 and the BOG that flows between the return valve 21 and the expansion device 23 in the return line 2. Do.
- the BOG that passes through the return line 2 is cooled by the BOG that passes through the first supply line 14.
- the temperature of the BOG flowing from the heat exchanger 22 in the return line 2, that is, the temperature T1 of the BOG in the portion 2 c between the heat exchanger 22 and the expansion device 23 in the return line 2 passes through the heat exchanger 22 in the return line 2. It depends on various factors such as the flow rate and pressure of the BOG and the flow rate and temperature of the BOG flowing into the heat exchanger 22 in the first supply line 14.
- the expansion device 23 expands the BOG flowing from the heat exchanger 22 along the return line 2. As a result, the BOG downstream of the expansion device 23 in the return line 2 is in a low-pressure and low-temperature gas-liquid two-phase state. Thus, the BOG flowing from the first supply line 14 to the return line is partially liquefied and returned to the tank 11.
- the expansion device 23 is, for example, an expansion valve, an ejector, or an expansion turbine.
- a pump 31 is disposed in the tank 11, and a forced vaporizer 32 that forcibly vaporizes LNG extracted from the pump 31 in the tank 11 is provided in the second supply line 15.
- the forced vaporizer 32 forcibly vaporizes LNG using, for example, steam generated in a boiler as a heat source, and generates VG.
- a device for example, a cooler and a gas-liquid separator for removing heavy components such as ethane from VG is provided in the downstream portion 15b of the second supply line 15 from the forced vaporizer 32. It is desirable. As a result, VG having a high methane number can be supplied to the auxiliary gas engine 13.
- a flow rate control valve 33 is provided on the upstream side portion 15a of the forced vaporizer 32 in the second supply line 15. The flow control valve 33 adjusts the amount of vaporized gas generated by the forced vaporizer 32.
- a first bridge line 41 is connected to the first supply line 14 from the second supply line 15.
- the first bridge line 41 is compressed in the first supply line 14 from the downstream portion 15b of the forced vaporizer 32 in the second supply line 15 when the BOG is insufficient with respect to the fuel gas consumption Q1 of the main gas engine 12.
- the VG is guided to the upstream portion 14a from the machine 16.
- BOG and VG are supplied as fuel gas to the main gas engine 12.
- the first bridge line 41 is provided with a first adjustment valve 42 whose opening degree can be changed.
- the second bridge line 43 is connected to the downstream portion 15 b from the forced vaporizer 32 in the second supply line 15.
- the second bridge line 43 guides the BOG from the compressor 16 to the second supply line 15 when the BOG is greater than the fuel gas consumption Q1 of the main gas engine 12.
- VG and BOG are supplied to the auxiliary gas engine 13 as fuel gas.
- the second bridge line 43 is provided with a second adjustment valve 44 whose opening degree can be changed.
- a first pressure gauge 51 is provided between the expansion device 23 and the return valve 21 in the return line 2.
- the first pressure gauge 51 detects the pressure p1 of BOG between the expansion device 23 and the return valve 21 in the return line 2.
- the first pressure gauge 51 is disposed in the portion 2 c between the expansion device 23 and the heat exchanger 22 in the return line 2, but is not limited thereto.
- the first pressure gauge 51 is The return line 2 may be disposed in a portion 2 b between the return valve 21 and the heat exchanger 22.
- a second pressure gauge 52 is provided in the upstream portion 2a of the return line 2 with respect to the return valve 21.
- the second pressure gauge 52 detects the BOG pressure p ⁇ b> 2 in the upstream portion 2 a of the return line 2 with respect to the return valve 21.
- the upstream portion 2 a of the return line 2 with respect to the return valve 21 communicates with the downstream portion 14 b of the first supply line 14 with respect to the compressor 16.
- the pressure p2 of the BOG detected by the second pressure gauge 52 is, so to speak, the pressure of the BOG in the downstream portion 14b of the compressor 16 in the first supply line 14 (that is, the BOG supplied to the main gas engine 12). It is.
- the pressure values detected by the first pressure gauge 51 and the second pressure gauge 52 are respectively sent to the control device 5.
- the return valve 21, the flow rate control valve 33, the first adjustment valve 42, and the second adjustment valve 44 described above are controlled by the control device 5.
- the controller 5 includes a first gas engine controller (not shown) for controlling the fuel gas injection timing of the main gas engine 12 and a second gas engine controller for controlling the fuel gas injection timing of the auxiliary gas engine 13.
- Various signals are transmitted from (not shown).
- the control device 5 calculates the fuel gas consumption Q1 of the main gas engine 12 from the signal transmitted from the first gas engine controller, and the auxiliary gas engine 13 from the signal transmitted from the second gas engine controller.
- the fuel gas consumption Q2 is calculated.
- the control device 5 may acquire the fuel gas consumption Q1 directly from the first gas engine controller, or may acquire the fuel gas consumption Q2 directly from the second gas engine controller. Good.
- the control device 5 opens the return valve 21 when at least one of the following conditions (A) to (D) is satisfied.
- the control device 5 controls the opening degree of the return valve 21 so that the BOG pressure p1 detected by the first pressure gauge 51 becomes the set pressure Ps while the return valve 21 is opened.
- the set pressure Ps is such that the flow rate of BOG that passes through the heat exchanger 22 in the return line 2 and the heat exchanger 22 in the first supply line 14 so that the reliquefaction rate of BOG that has passed through the expansion device 23 increases. Is appropriately set according to various factors such as the flow rate and temperature of the BOG flowing into the.
- the set pressure Ps is set to a pressure higher than the supercritical pressure Pc.
- the set pressure Ps may be a pressure equal to or lower than the supercritical pressure Pc.
- the control device 5 increases the opening degree of the return valve 21 in preference to the control based on the set pressure Ps described above. Specifically, the control device 5 increases the opening degree of the return valve 21 when the pressure P2 of the BOG detected by the second pressure gauge 52 exceeds the threshold value PTH.
- the control start is in the middle of the return control
- the return valve 21 may start from the intermediate opening
- the control start is before the return control starts
- the return valve 21 starts from the fully closed state. May be.
- FIG. 2 a change in state of the BOG when the BOG is returned to the tank 11 through the return line 2 without pressure reduction by the return valve 21 is indicated by a one-dot chain line.
- the isothermal lines LT1 to LT3 for the BOG temperatures T1 to T3 are indicated by thin solid lines.
- a low-pressure and low-temperature saturated (point A) BOG flows from the tank 11 into the heat exchanger 22 through the first supply line 14 and is heated by exchanging heat with the high-pressure and high-temperature BOG flowing through the return line 2 ( Superheated) (point A ⁇ point B). Thereafter, the BOG is compressed to a supercritical state by the compressor 16 (point B ⁇ point C). The BOG flowing into the return line 2 from the first supply line 14 is reduced to the set pressure Ps by the return valve 21, and the temperature of the BOG decreases from the temperature T3 to the temperature T2 (point C ⁇ point D).
- the BOG decompressed by the return valve 21 is cooled by the heat exchanger 22, and the temperature of the BOG decreases from the temperature T2 to the temperature T1 (point D ⁇ point E).
- BOG is liquefied by cooling in the heat exchanger 22.
- the liquid BOG flowing from the heat exchanger 22 is expanded by the expansion device 23 to be in a low-pressure and low-temperature gas-liquid two-phase state (point E ⁇ point F).
- the BOG reliquefaction rate in the present embodiment is obtained when BOG is returned to the tank 11 through the return line 2 without pressure reduction by the return valve 21 (point C ⁇ point E ′ ⁇ point F ′).
- the reliquefaction rate becomes larger.
- the control device 5 returns the return valve 21 so that the pressure p1 of the BOG flowing between the return valve 21 and the expansion device 23 in the return line 2 becomes the set pressure Ps. Therefore, the BOG reliquefaction rate after passing through the expansion device 23 can be improved. For example, if the absolute amount of cold heat is the same, the amount of return gas that can be cooled to point E decreases, but the liquefaction rate increases and the amount of liquefaction increases.
- the control device 5 increases the opening degree of the return valve 21 when the BOG pressure p2 detected by the second pressure gauge 52 exceeds the threshold PTH, the pressure p2 increases. If it is too much, an increase in the pressure p2 is suppressed, and in other cases, the above effect can be obtained.
- the BOG flowing through the return line 2 can be cooled using the BOG flowing through the upstream portion 14a of the first supply line 14 from the compressor 16.
- heat exchange is performed between the BOG flowing between the return valve 21 and the expansion device 23 in the return line 2 and the LNG flowing through the second supply line 15.
- a heat exchanger 24 for performing is provided.
- a heat exchanger for cooling the BOG flowing between the return valve 21 and the expansion device 23 in the return line 2 is not provided, or a heat exchanger through which the BOG guided from the tank 11 to the compressor 16 passes is not provided.
- the state change of the BOG of the present embodiment is different from the state change of the BOG of the first embodiment shown in FIG. Therefore, in the present embodiment, the set pressure Ps different from that in the first embodiment is appropriately set according to the various elements described above so that the reliquefaction rate of the BOG that has passed through the expansion device 23 increases.
- the same effect as in the first embodiment can be obtained.
- the BOG flowing through the return line 2 can be cooled using LNG flowing through the second supply line 15.
- the control device 5 increases the opening degree of the return valve 21 when the BOG pressure p2 detected by the second pressure gauge 52 exceeds the threshold value PTH.
- the present invention is not limited to this.
- the control device 5 maintains the BOG pressure p1 detected by the first pressure gauge 51 at the set pressure Ps, and the compressor 16 in the first supply line 14 when the pressure p2 exceeds the threshold value PTH. You may control so that BOG of the more downstream part 14b may be escaped to a gas combustion apparatus etc. (not shown).
- the compressor 16 compresses BOG to a pressure higher than the supercritical pressure Pc.
- the fuel gas injection pressure of the main gas engine 12 is medium pressure (for example, 1 to 1).
- the pressure p2 supplied from the compressor 16 to the main gas engine 12 may be lower than the supercritical pressure Pc.
- the return line 2 may be provided with both the heat exchanger 22 of the first embodiment and the heat exchanger 24 of the second embodiment.
- the heat exchanger 22 and the heat exchanger 24 may be provided separately in the return line 2 or may be provided integrally in the return line 2.
- the first bridge line 41 may be provided with a pressure reducing valve that outputs a constant secondary pressure even when the primary pressure fluctuates, and a check valve, instead of the first regulating valve 42. According to this configuration, VG is automatically replenished when the pressure of BOG flowing through the upstream portion 14a of the first supply line 14 from the compressor 16 is lower than the secondary pressure of the pressure reducing valve.
- main gas engine 12 and the auxiliary gas engine 13 are not necessarily a reciprocating engine, and may be a gas turbine engine.
- the gas engine of the present invention may not be a main gas engine for propulsion, and may be a gas engine for inboard power, for example.
- the present invention is also applicable to a ship that does not have the first bridge line 41 and / or the second bridge line 43. Furthermore, the present invention is also applicable to the auxiliary gas engine 13 and a ship that does not have the second supply line 15 for supplying VG thereto.
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- General Engineering & Computer Science (AREA)
- Ocean & Marine Engineering (AREA)
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Abstract
Description
図1に、本発明の第1実施形態に係る船舶1Aを示す。この船舶1Aは、液化天然ガス(以下、LNGという)を貯留するタンク11と、推進用の主ガスエンジン12と、発電用(すなわち、船内電源用)の副ガスエンジン13を含む。
(A)第2ブリッジライン43から副ガスエンジン13にBOGを供給していない場合、タンク11内のLNGの量およびタンク11内のBOGの圧力から算出されたBOGの利用可能量Qaが、主ガスエンジン12の燃料ガス消費量Q1より大きいとき
(B)第2ブリッジライン43から副ガスエンジン13にBOGを供給している場合、主ガスエンジン12の燃料ガス消費量Q1と副ガスエンジン13の燃料ガス消費量Q2の総計よりBOGの利用可能量Qaが大きいとき
(C)タンク11内のBOGの圧力が所定の圧力より大きいとき
(D)主ガスエンジン12の負荷が所定の割合(例えば70%)より低いとき
次に、図3を参照して、本発明の第2実施形態に係る船舶1Bを説明する。なお、本実施形態において、第1実施形態と同一構成要素には同一符号を付し、重複した説明は省略する。
上記実施形態は、全ての点で例示であって、制限的なものではないと考えられるべきである。本発明の範囲は、上述の説明ではなくて特許請求の範囲によって示され、特許請求の範囲と均等の意味および範囲内でのすべての変更が含まれることが意図される。
11 タンク
12 主ガスエンジン(ガスエンジン)
13 副ガスエンジン
14 第1供給ライン(供給ライン)
15 第2供給ライン
16 圧縮機
2 返送ライン
21 返送弁
22,24 熱交換器
5 制御装置
51 第1圧力計(圧力計)
52 第2圧力計
Claims (4)
- ガスエンジンと、
液化天然ガスを貯留するタンクと、
前記タンク内で発生したボイルオフガスを燃料ガスとして前記ガスエンジンへ導く、圧縮機が設けられた供給ラインと、
前記圧縮機よりも下流側で前記供給ラインから分岐して前記タンクへつながる、膨張装置が設けられた返送ラインと、
前記返送ラインにおける前記膨張装置よりも上流側部分に設けられた、開度変更可能な返送弁と、
前記返送ラインにおける前記返送弁と前記膨張装置との間を流れるボイルオフガスと熱媒体との間で熱交換を行う熱交換器と、
前記返送ラインにおける前記返送弁と前記膨張装置との間を流れるボイルオフガスの圧力を検出する圧力計と、
前記圧力計により検出されるボイルオフガスの圧力が設定圧力となるように前記返送弁を制御する制御装置と、を備える、船舶。 - 前記圧力計は、第1圧力計であり、前記船舶は、前記供給ラインにおける前記圧縮機よりも下流側部分を流れるボイルオフガスの圧力を検出する第2圧力計を更に備え、
前記制御装置は、前記第2圧力計により検出されるボイルオフガスの圧力が閾値を上回ったときに、前記設定圧力に基づく制御に優先して前記返送弁の開度を増大させる、請求項1に記載の船舶。 - 前記熱交換器は、前記返送ラインにおける前記返送弁と前記膨張装置との間を流れるボイルオフガスと前記供給ラインにおける前記圧縮機よりも上流側部分に流れるボイルオフガスとの間で熱交換を行う、請求項1または2に記載の船舶。
- 前記ガスエンジンは、主ガスエンジンであり、前記供給ラインは、第1供給ラインであり、
前記船舶は、発電用の副ガスエンジンと、前記タンク内から液化天然ガスを取り出し、その液化天然ガスが気化した気化ガスを燃料ガスとして前記副ガスエンジンへ導く第2供給ラインと、を備え、
前記熱交換器は、前記返送ラインにおける前記返送弁と前記膨張装置との間を流れるボイルオフガスと前記第2供給ラインを流れる液化天然ガスとの間で熱交換を行う、請求項1~3のいずれか一項に記載の船舶。
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CN201680073134.3A CN108368797B (zh) | 2015-12-18 | 2016-12-14 | 船舶 |
KR1020187019551A KR20180090369A (ko) | 2015-12-18 | 2016-12-14 | 선박 |
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JP7316068B2 (ja) * | 2019-03-15 | 2023-07-27 | 三菱重工マリンマシナリ株式会社 | 浮体式設備及び浮体式設備の製造方法 |
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JPS62243936A (ja) * | 1986-04-16 | 1987-10-24 | Mitsubishi Heavy Ind Ltd | 機関の燃料制御装置 |
JP2011011701A (ja) * | 2009-07-06 | 2011-01-20 | Ihi Marine United Inc | ガス焚き超電導電気推進船 |
JP2013210148A (ja) * | 2012-03-30 | 2013-10-10 | Mitsubishi Heavy Ind Ltd | 船舶、燃料供給装置、推進用主機への液化燃料ガスの供給方法 |
JP2015158263A (ja) * | 2014-02-25 | 2015-09-03 | 三井造船株式会社 | ボイルオフガス回収システム |
JP2015535913A (ja) * | 2012-10-24 | 2015-12-17 | デウ シップビルディング アンド マリーン エンジニアリング カンパニー リミテッド | 船舶の液化ガス処理システム |
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CN104265512B (zh) * | 2014-09-17 | 2017-05-24 | 刘国满 | 一种船舶动力装置的高压/低压燃气供应系统 |
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2015
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2016
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JPS62243936A (ja) * | 1986-04-16 | 1987-10-24 | Mitsubishi Heavy Ind Ltd | 機関の燃料制御装置 |
JP2011011701A (ja) * | 2009-07-06 | 2011-01-20 | Ihi Marine United Inc | ガス焚き超電導電気推進船 |
JP2013210148A (ja) * | 2012-03-30 | 2013-10-10 | Mitsubishi Heavy Ind Ltd | 船舶、燃料供給装置、推進用主機への液化燃料ガスの供給方法 |
JP2015535913A (ja) * | 2012-10-24 | 2015-12-17 | デウ シップビルディング アンド マリーン エンジニアリング カンパニー リミテッド | 船舶の液化ガス処理システム |
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CN110939531A (zh) * | 2018-09-21 | 2020-03-31 | 罗伯特·博世有限公司 | 用于内燃机的燃料输送装置 |
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JP6670088B2 (ja) | 2020-03-18 |
KR20180090369A (ko) | 2018-08-10 |
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