KR20230087633A - Fuel providing system of ship - Google Patents

Abstract

Disclosed is a fuel supply system for a ship. According to an embodiment of the present invention, the fuel supply system for a ship comprises: a boil-off gas compressor compressing boil-off gas supplied from a storage tank; a mixer mixing the compressed boil-off gas with liquefied gas supplied from an inner pump of the storage tank, and condensing the mixture; a pressing pump pressing the mixed fluid passing through the mixer to meet a fuel supply condition of a first consumer; a heat exchange unit recollecting cold heat from the mixed fluid passing through the heat exchange unit; a first gasifier gasifying the mixed fluid passing through the heat exchange unit to meet a fuel supply condition of the first consumer; a subcooler which subcools a part of the mixed fluid passing through the mixer by exchanging heat with a refrigerant; and a recollection line connecting the subcooler and the storage tank, and recollecting the mixed fluid passing through the subcooler into the storage tank. Therefore, the overall system efficiency can be improved.

Description

Ship's fuel supply system {FUEL PROVIDING SYSTEM OF SHIP}

The present invention relates to a fuel supply system for ships.

As the regulations of the International Maritime Organization (IMO) on the emission of greenhouse gases and various air pollutants are strengthened, the shipbuilding and shipping industries use natural gas, a clean energy source, instead of using heavy oil and diesel oil, which are conventional fuels. It is increasingly used as a fuel gas for ships.

Natural gas, which is widely used among fuel gases, has methane as its main component, and is usually converted to a liquefied gas state whose volume is reduced to 1/600 and stored in a storage tank. At this time, external heat is continuously transferred into the storage tank to generate evaporation gas, and the evaporation gas may cause deformation and damage of the storage tank by increasing the internal pressure of the storage tank.

Accordingly, conventionally, the boil-off gas is supplied from the storage tank, compressed to high pressure by a compression unit including a multi-stage compressor, and supplied to the high-pressure injection engine, but the boil-off gas exceeding the fuel supply required by the engine is re-liquefied. After the gas-liquid separation, the liquid component is recovered to the storage tank, and the gas component is sent to the compression unit again. At this time, the liquid component recovered to the storage tank can be injected into the storage tank to suppress the generation of boil-off gas, and the gas component is sent to the compression unit together with the boil-off gas to be compressed to a high pressure in accordance with the fuel supply conditions of the engine.

However, this prior art has a problem in that energy consumption is high and the efficiency of the entire system is reduced because the fluid must be compressed at a high pressure by continuously operating the compression unit.

As a related technology, please refer to Korean Patent Publication No. 10-2014-0075584 (published on June 19, 2014).

Korean Patent Publication No. 10-2014-0075584 (published on June 19, 2014)

An embodiment of the present invention is to provide a fuel supply system for a ship that can reduce the amount of boil-off gas generated inside the storage tank and improve the efficiency of the entire system in supplying fuel to demand.

According to one aspect of the present invention, the boil-off gas compressor for compressing the boil-off gas supplied from the storage tank; a mixer for condensing the compressed boil-off gas by mixing it with liquefied gas supplied from the internal pump of the storage tank; a pressurization pump that pressurizes the mixed fluid that has passed through the mixer according to fuel supply conditions of a first consumer; a heat exchange unit that recovers cold heat from the mixed fluid passing through the pressure pump; a first vaporizer that vaporizes the mixed fluid that has passed through the heat exchanger in accordance with the fuel supply conditions of the first consumer; a supercooler for subcooling a part of the mixed fluid passing through the mixer by heat exchange with a refrigerant; and a recovery line connecting the supercooler and the storage tank and recovering the mixed fluid passing through the supercooler into the storage tank.

The evaporation gas compressor compresses the evaporation gas supplied from the storage tank to a low pressure according to the operating conditions of the mixer, and heat-exchanges the evaporation gas compressed by the evaporation gas compressor with the evaporation gas supplied from the storage tank to cool An evaporation gas cooling and heat recovery unit, a compression line for supplying the evaporation gas supplied from the storage tank to the evaporation gas compressor through the evaporation gas cold and heat recovery unit, and the evaporation gas cold and heat recovery of the evaporation gas compressed by the evaporation gas compressor It may further include a main supply line supplying the mixer to the mixer through a unit and connecting the mixer, the pressure pump, the heat exchange unit, the first vaporizer, and the first consumer.

A first low-pressure fuel line branched from the rear end of the evaporative gas compressor of the main supply line and connected to a second consumer that uses a lower pressure fuel gas than the first consumer, and is provided in the main supply line, and the evaporative gas compressor A first measurement unit for measuring the flow rate passing through the first low-pressure fuel line is provided, and when the measured flow rate exceeds a set fuel supply amount, at least a portion of the boil-off gas compressed by the boil-off gas compressor is supplied to the third fuel line. It may further include a first control valve that is opened to be supplied to the second consumer.

The main supply line is branched from the front end of the pressure pump and connected to a second consumer using low-pressure fuel gas through the heat exchange unit, and at least a part of the mixed fluid passing through the mixer is heated by the heat exchange unit. A second low-pressure fuel line supplied to the second consumer, and a second vaporizer provided in the second low-pressure fuel line and vaporizing the mixed fluid that has passed through the heat exchanger to a low pressure suitable for the fuel supply conditions of the second consumer. can include

The fuel replenishment line branched from the rear end of the boil-off gas compressor of the main supply line and connected to the rear end of the first vaporizer of the main supply line, and the boil-off gas compressed by the boil-off gas compressor provided in the fuel replenishment line to the first consumer. A booster compressor for compressing fuel supply conditions may be further included.

The evaporation gas compressor compresses to a high pressure in accordance with the fuel supply conditions of the first consumer, is provided at the rear end of the evaporation gas compressor in the main supply line, and transfers the pressure of the evaporation gas compressed by the evaporation gas compressor to the mixer. A second control valve for converting to suit operating conditions, branched from the rear end of the boil-off gas compressor of the main supply line and connected to the rear end of the heat exchange part of the main supply line, to meet the fuel consumption of the first consumer, A fuel replenishment line for supplying at least a portion of the boil-off gas compressed by the boil-off gas compressor toward the first consumer may be further included.

It further includes a refrigerant circulation line for circulating the refrigerant, wherein an expander, a refrigerant compressor, and a refrigerant cooler for expanding, compressing, and cooling the refrigerant are provided in the refrigerant circulation line, and the refrigerant expanded by the expander is transferred by the heat exchange unit. After primary heat exchange with the mixed fluid flowing along the recovery line, secondary heat exchange with the refrigerant that has passed through the refrigerant cooler is used to recover cold heat, and then circulates toward the expander through the refrigerant compressor, the refrigerant cooler, and the heat exchange unit.

The mixer may be a recondenser or an inline type mixer.

The ship's fuel supply system according to an embodiment of the present invention can reduce the amount of evaporation gas generated inside the storage tank and improve the overall system efficiency in supplying fuel to a demand place.

In addition, it is possible to receive liquefied gas through a pump inside the storage tank with less energy consumption than the conventional compression unit, mix it with boil-off gas compressed to a low pressure, pressurize it, and then supply it as fuel to the first consumer.

In addition, it can be effectively used to suppress the amount of evaporation gas generated inside the storage tank by supercooling the mixed fluid that has passed through the mixer.

The effects of the present invention are not limited to the effects mentioned above, and other effects not mentioned will be clearly understood by those skilled in the art from the description of the claims.

1 shows a fuel supply system for a ship according to an embodiment of the present invention.
FIG. 2 shows a form in which a configuration for supplying fuel to a customer requiring low-pressure fuel gas is applied to the fuel supply system of FIG. 1 .
FIG. 3 shows a configuration in which the fuel supply system of FIG. 1 compresses boil-off gas step by step and supplies fuel to a customer requiring high-pressure fuel gas.
FIG. 4 shows a configuration in which the fuel supply system of FIG. 1 compresses boil-off gas at a high pressure and supplies it to a consumer or adjusts the pressure of the compressed boil-off gas and supplies it to a mixer.
FIG. 5 shows an integrated form of heat exchanging means provided in the fuel supply system of FIG. 1 .

Hereinafter, embodiments of the present invention will be described in detail with reference to the accompanying drawings. The embodiments introduced below are provided as examples to sufficiently convey the spirit of the present invention to those skilled in the art. The present invention is not limited to the embodiments described below and may be embodied in other forms. In order to clearly explain the present invention, parts irrelevant to the description are omitted from the drawings, and in the drawings, the width, length, thickness, etc. of components may be exaggerated for convenience. Like reference numbers indicate like elements throughout the specification.

1 shows a fuel supply system for a ship according to an embodiment of the present invention.

Referring to FIG. 1, the ship's fuel supply system 100 according to an embodiment of the present invention includes a boil-off gas compressor 110 for compressing boil-off gas supplied from a storage tank 101 and a boil-off gas compressor 110. Mixer 120 for condensing the boil-off gas compressed by the mixture with liquefied gas supplied from the internal pump P of the storage tank 101, and the mixed fluid passing through the mixer 120 to the first consumer E1 A pressurization pump 130 that pressurizes fuel supply conditions, a heat exchange unit 140 that recovers cold heat from the mixed fluid that has passed through the pressurization pump 130, and the mixed fluid that has passed through the heat exchange unit 140 is transferred to a first consumer. A first vaporizer 160 that vaporizes according to the fuel supply condition of (E1), a supercooler 125 that supercools a part of the mixed fluid passing through the mixer 120 by heat exchange with a refrigerant, and a supercooler 125 ) and the storage tank 101, and includes a recovery line L10 for recovering the mixed fluid that has passed through the supercooler 125 into the storage tank 101.

Here, the boil-off gas compressor 110 may be a means for compressing the boil-off gas supplied from the storage tank 101 to a low pressure in accordance with the operating conditions of the mixer 120.

In addition, the fuel supply system 100 includes an boil-off gas cooling and heat recovery unit 105 for cooling the boil-off gas compressed by the boil-off gas compressor 110 by heat exchange with boil-off gas supplied from the storage tank 101, and a storage tank ( 101) and the compression line (L11) for supplying the boil-off gas supplied from the boil-off gas cooling and heat recovery unit 105 to the boil-off gas compressor 110, and the boil-off gas compressed by the boil-off gas compressor 110 It is supplied to the mixer 120 through the recovery unit 105, and the main supply connecting the mixer 120, the pressure pump 130, the heat exchange unit 140, the first vaporizer 160, and the first consumer E1. line L12.

In addition, the fuel supply system 100 is branched from the rear end of the boil-off gas compressor 110 of the main supply line L12 and is connected to the second consumer E2 using a lower pressure fuel gas than the first consumer E1. 1 is provided in the low-pressure fuel line (L13), the main supply line (L12), and the first measuring unit (Q1) for measuring the flow rate passing through the boil-off gas compressor 110, and the first low-pressure fuel line (L13) Provided, when the flow rate measured by the first measuring unit (Q1) exceeds the set fuel supply amount, at least a part of the boil-off gas compressed by the boil-off gas compressor 110 is opened to be supplied to the second consumer (E2) It may include a first control valve (V1).

Hereinafter, each component of the ship's fuel supply system 100 will be described in detail.

Referring to FIG. 1, the ship's fuel supply system 100 includes, for example, a liquefied fuel carrier, a liquefied fuel RV (Regasification Vessel), a container ship, a general merchant ship, an LNG Floating, Production, Storage and Off-loading (FPSO), and an LNG FSRU. (Floating Storage and Regasification Unit) and the like can be provided in various ships.

The storage tank 101 may store LNG (Liquefied Natural Gas) as liquefied gas, for example, and may include a membrane type tank, an SPB type tank, etc. for storing fuel in a liquefied state while maintaining an adiabatic state.

The boil-off gas of the liquefied gas stored in the storage tank 101 is supplied to the boil-off gas compressor 110 through the boil-off gas cold heat recovery unit 105 through the compression line L11, and the liquefied gas stored in the storage tank 101 It is pumped by the internal pump P of the storage tank 101 and supplied to the mixer 120 through the pumping line L17.

The pump P provided inside the storage tank 101 may pressurize and pump the liquefied gas to about 8 barg, for example, and the liquefied gas is supplied to the mixer 120 through the pumping line L17.

The boil-off gas of the liquefied gas stored in the storage tank 101 flows to the boil-off gas compressor 110 in a heated state by heat exchange while passing through the boil-off gas cold heat recovery unit 105 through the compression line L11. Here, the compression line (L11) connects the storage tank 101, the boil-off gas cold heat recovery unit 105, and the boil-off gas compressor 110.

The evaporation gas compressor 110 may compress the evaporation gas passing through the evaporation gas cooling and heat recovery unit 105 to a low pressure according to the operating conditions of the mixer 120 . The evaporation gas compressor 110 may compress the evaporation gas that has passed through the evaporation gas cooling and heat recovery unit 105 to about 5.6 barg, for example.

The boil-off gas compressed by the boil-off gas compressor 110 exchanges heat with the boil-off gas flowing through the compression line L11 by the boil-off gas cold heat recovery unit 105 to recover the cold heat and through the main supply line L12. It flows and is supplied to the mixer 120. The main supply line (L12) is the evaporation gas compressor 110, the evaporation gas cold heat recovery unit 105, the mixer 120, the pressure pump 130, the heat exchange unit 140, the first vaporizer 160, and the first demand place Connect (E1).

Here, when the amount of boil-off gas generated in the storage tank 101 exceeds the amount of fuel supply required by the first consumer (E1), the main supply line (L12) is branched from the rear end of the boil-off gas compressor (110) to the first consumer (E1). An excess amount of boil-off gas may be supplied toward the first low-pressure fuel line L13 connected to the second consumer E2 using low-pressure fuel gas compared to (E1).

The first measuring unit (Q1) is provided in the main supply line (L12) to measure the flow rate passing through the boil-off gas compressor 110, and the first control valve (V1) provided in the first low-pressure fuel line (L13) is When the flow rate measured by the measurement unit Q1 exceeds the set fuel supply amount, at least a portion of the boil-off gas compressed by the boil-off gas compressor 110 is opened to be supplied to the second consumer E2. The second consumer E2 may include an engine for power generation using a lower pressure fuel gas than the first consumer E1.

After the boil-off gas compressed to a low pressure by the boil-off gas compressor 110 is mixed with liquefied gas by the mixer 120, the first consumer (E1) requiring higher pressure fuel than the second consumer (E2) The fuel may be converted to suit the fuel supply conditions and supplied toward the first consumer E1. The first consumer (E1) is, for example, a high-pressure (approximately 150-700 bar) injection engine such as ME-GI engine (Man B&W's gas injection engine) and a medium-pressure (approximately 16-18 bar) fuel gas that is an X-DF engine. may include a medium-pressure gas injection engine capable of

Conventionally, the boil-off gas had to be compressed at a high pressure according to the fuel supply conditions of the customer through the compression section including multi-stage compressors, so the load on the compression section was large, and some of the boil-off gas compressed at high pressure was re-liquefied and returned to the storage tank. Even in this case, the pressure and temperature had to be dropped rapidly.

However, since the boil-off gas is compressed to a low pressure by the first-stage boil-off gas compressor 110 through an embodiment of the present invention, energy consumption by the boil-off gas compressor 110 can be reduced.

The mixer 120 mixes the boil-off gas compressed by the boil-off gas compressor 110 and the liquefied gas supplied through the pump P in the storage tank 101. Through this, condensation of the boil-off gas can be achieved.

The mixer 120 may include, for example, a recondenser type or an in-line type mixer. The mixer of the recondenser type is in the form of a drum having a packing inside.

In addition, the mixer of the recondenser type can stably supply the mixed fluid toward the booster pump (130). For example, a recondenser-type mixer may perform an operation of separating gas-liquid when gas-liquid mixing is not smoothly performed.

In addition, the recondenser type mixer can serve as a buffer tank to prevent gas from entering until the operation of the pressure pump 130 is stopped when the pump P in the storage tank 101 is stopped. there is.

The mixer of the in-line type (or also called static type) is a type in which the packing is filled in the pipe, and the boil-off gas and the liquefied gas are introduced into the pipe and mixed. In the case of using an in-line mixer, the volume and weight are reduced to almost 1/10 compared to other mixers, so when installed on a ship, the installation space can be reduced and the unit price is low.

Some of the mixed fluid passing through the mixer 120 may be recovered into the storage tank 101 through the supercooler 125 through the recovery line L10.

The recovery line (L10) is branched from the rear end of the mixer 120 of the main supply line (L12) and transfers the flow rate exceeding the fuel supply amount required by the first consumer (E1) among the fluids mixed by the mixer 120 to the supercooler Through (125) it can be recovered into the storage tank (101).

The supercooler 125 subcools a part of the mixed fluid that has passed through the mixer 120 by heat exchange with a refrigerant. The supercooled mixed fluid can be used to suppress the amount of evaporation gas generated inside the storage tank 101 . The supercooler 125 may perform a supercooling process based on a known reverse Brayton cycle.

An injection unit 127 is provided at the end of the recovery line L10 to inject the mixed fluid supercooled by the supercooler 125 into the storage tank 101 . The injection unit 127 may include, for example, injection nozzles, and may be provided in plurality.

The pressure pump 130 pressurizes the fluid mixed by the mixer 120 according to the fuel supply conditions of the first consumer E1. The pressurization pump 130 may pressurize the mixed fluid according to fuel supply conditions of the first consumer E1 including a high-pressure injection engine such as an ME-GI engine.

The heat exchanger 140 exchanges heat with the refrigerant for the mixed fluid that has passed through the pressure pump 130 to recover cold heat from the mixed fluid. Here, the refrigerant is circulated and supplied along the refrigerant circulation line (L16).

An expander 152, a refrigerant compressor 154, and a refrigerant cooler 156 are provided in the refrigerant circulation line L16 to expand, compress, and cool the refrigerant. The refrigerant compressor 154 is axially connected to the expander 152 and may be driven using expansion energy of the expander 152 .

The refrigerant expanded by the expander 152 undergoes primary heat exchange with the mixed fluid flowing along the recovery line L10 by the supercooler 125, and then the refrigerant passed through the refrigerant cooler 156 by the heat exchange unit 140 The cold heat is recovered through secondary heat exchange with the refrigerant, and then circulates toward the expander 152 through the refrigerant compressor 154, the refrigerant cooler 156, and the heat exchanger 140. Nitrogen, propane, propylene, ammonia, butane, butadiene, or mixtures thereof may be used as the refrigerant.

Specifically, the temperature of the refrigerant expanded by the expander 152 is converted to approximately -153 ° C after passing through the supercooler 125 at approximately -173 ° C, and passes through the refrigerant cooler 156 in the heat exchange unit 140 It is converted to approximately 21 ° C by secondary heat exchange with one refrigerant. Then, the refrigerant flows into the compressor 154 and is converted to approximately 85 ° C, converted to approximately 35 ° C through the refrigerant cooler 156, and then converted to -146 ° C through a heat exchange process in the heat exchange unit 140 and then converted to the expander It cycles to (152).

The mixed fluid passing through the pressure pump 130 described above exchanges heat with the refrigerant that has passed through the refrigerant cooler 156 by the heat exchanger 140 at approximately -123 ° C and is converted to approximately 21 ° C, and then the first consumer E1 ) Flows to the first vaporizer 160 that vaporizes according to the fuel supply conditions.

The mixed fluid passing through the first vaporizer 160 may be converted to approximately 45° C. and then supplied as fuel to the first consumer E1.

FIG. 2 shows a form in which a configuration for supplying fuel to a customer requiring low-pressure fuel gas is applied to the fuel supply system of FIG. 1 .

Referring to FIG. 2, the fuel supply system 100 is branched from the front end of the pressure pump 130 of the main supply line L12 and connected to the second consumer E2 using low-pressure fuel gas via the heat exchange unit 140. A second low-pressure fuel line (L14) for supplying at least a part of the mixed fluid that has passed through the mixer 120 to the second consumer (E2) in a heated state by the heat exchanger 140, and a second low-pressure fuel It is provided in the line L14 and may include a second vaporizer 170 that vaporizes the mixed fluid that has passed through the heat exchanger 140 at a low pressure in accordance with the fuel supply conditions of the second consumer E2.

Specifically, when the amount of boil-off gas generated inside the storage tank 101 is less than the set value, at least a portion of the fluid mixed by the mixer 120 is supplied and vaporized by the second vaporizer 170 to supply the second low-pressure fuel line ( It can be supplied to the second consumer (E2) through L14).

At this time, the fluid mixed by the mixer 120 exchanges heat with the refrigerant that has passed through the refrigerant cooler 156 in the heat exchange unit 140 and is vaporized by the second vaporizer 170 in a state in which cooling heat is deprived (heating state). It is supplied to the second consumer (E2), and since the refrigerant is circulated toward the expander 152 in a state where the temperature has dropped, the load required for cooling the refrigerant can be reduced.

FIG. 3 shows a configuration in which the fuel supply system of FIG. 1 compresses boil-off gas step by step and supplies fuel to a customer requiring high-pressure fuel gas.

Referring to FIG. 3, the fuel supply system 100 is branched from the rear end of the boil-off gas compressor 110 of the main supply line L12 and connected to the rear end of the first vaporizer 160 of the main supply line L12. L15) and a booster compressor (180, Booster Compressor) provided in the fuel replenishment line (L15) and pressurizing the boil-off gas compressed by the boil-off gas compressor 110 according to the fuel supply conditions of the first consumer (E1) can include

For example, when the fuel consumption of the first consumer E1 is greater than the supplied fuel or when the use of the supercooler 125 is impossible, the evaporation gas compressor 110 and the booster compressor 180 step by step pressurization and control Boiled gas converted to meet the fuel supply conditions of the first consumer E1 may be additionally supplied through the fuel replenishment line L15.

Although not shown, the above-described fuel replenishment line (L15) may be branched from the front end of the evaporative gas compressor 110 of the compression line (L11) in another example, and in this case, the first demand source alone by the booster compressor 180 Pressurization of the boil-off gas may be performed according to the fuel supply condition of (E1).

FIG. 4 shows a configuration in which the fuel supply system of FIG. 1 compresses boil-off gas at a high pressure and supplies it to a consumer or adjusts the pressure of the compressed boil-off gas and supplies it to a mixer.

On the other hand, the above-described boil-off gas compressor 110 may be a means for compressing the fuel to a high pressure (or medium pressure) in accordance with the fuel supply conditions of the first consumer (E1).

In this case, referring to FIG. 4, the fuel supply system 100 is provided at the rear end of the boil-off gas compressor 110 of the main supply line (L12), and the pressure of the boil-off gas compressed by the boil-off gas compressor 110 is mixed with a mixer ( 120) and the second control valve (V2) for conversion according to the operating conditions, and the rear end of the heat exchange unit 140 of the main supply line (L12) branched from the rear end of the boil-off gas compressor 110 of the main supply line (L12) and connected, and includes a fuel replenishment line (L15) for supplying at least some of the boil-off gas compressed by the boil-off gas compressor 110 toward the first consumer (E1) in order to satisfy the fuel consumption of the first consumer (E1). can do.

Through this configuration, the fuel supply system 100 can be efficiently operated even when the fuel consumption of the first consumer E1 is greater than the supplied fuel or when the supercooler 125 cannot be used.

FIG. 5 shows an integrated form of heat exchanging means provided in the fuel supply system of FIG. 1 .

Referring to FIG. 5 , the fuel supply system 100 may integrate the supercooler 125 and the heat exchange unit 140 shown in FIG. 1 into one heat exchange unit 140 .

In this case, some of the fluids mixed through the mixer 120 flow to the heat exchange unit 140 through the recovery line L10 and are cooled by heat exchange with the refrigerant that has passed through the expander 152, and then stored in the storage tank 101. returned to the inside

In addition, the mixed fluid passing through the pressure pump 130 of the main supply line (L12) flows to the heat exchange unit 140 and is heated by heat exchange with the refrigerant passing through the refrigerant cooler 156, and then the first vaporizer 160 supplied with Since the circulating supply process of the refrigerant has been described with reference to FIG. 1, it will be omitted below.

On the other hand, the second measuring device (Q2) for measuring the pressure of the storage tank 101, provided at the rear end of the boil-off gas compressor 110 of the main supply line (L12), according to the pressure measured by the second measuring device (Q2) Accordingly, a third control valve V3 for controlling the amount of boil-off gas supplied to the mixer 120 may be provided.

In addition, a third measuring device (Q3) provided at the rear end of the mixer 120 of the main supply line (L12) to measure the temperature of the fluid mixed by the mixer 120, and provided at the pumping line (L17), the third measuring device A fourth control valve (V4) may be provided to adjust the amount of liquefied gas supplied to the mixer 120 according to the temperature of the mixed fluid measured by (Q3).

If the temperature of the fluid mixed by the mixer 120 is lower than the set value, the efficiency of the supercooler 125 may decrease. To prevent this, as described above, the second measuring device Q2 and the third measuring device Q3 Opening and closing degrees of the third control valve V3 and the fourth control valve V4 may be controlled according to the measured value.

In this way, through the above-described embodiment of the present invention, the liquefied gas supplied through the internal pump P of the storage tank 101, which consumes less energy than the conventional compression unit, is mixed with the boil-off gas compressed to a low pressure and pressurized. After that, it can be supplied to the consumer (E1), so the overall energy efficiency can be improved.

In addition, for a flow rate exceeding the fuel supply amount of the first consumer E1 among the fluids mixed by the mixer 120, the amount of boil-off gas generated can be effectively suppressed by supercooling and spraying it into the storage tank 101.

In addition, the supercooling efficiency can be improved by adjusting the flow rate of the liquefied gas supplied to the mixer 120 according to the temperature of the fluid mixed by the mixer 120 .

In addition, when the amount of boil-off gas generated inside the storage tank 101 exceeds the set value, the boil-off gas compressed by the boil-off gas compressor 110 is sent to the second consumer (E2) requiring low-pressure fuel, and the storage tank 101 ) Internal pressure control and boil-off gas treatment can be effectively performed.

In addition, the boil-off gas boosted by the booster compressor 180 can be supplemented with fuel, so when the fuel consumption of the first consumer E1 is greater than the boil-off gas generation or when the supercooler 125 cannot be used can be dealt with effectively.

In the above, specific embodiments have been illustrated and described. However, the present invention is not limited to the above-described embodiments, and those skilled in the art can make various changes without departing from the gist of the technical idea set forth in the claims below. You will be able to.

101: storage tank 105: boil-off gas cold heat recovery unit
110: boil-off gas compressor 120: mixer
125: supercooler 130: pressure pump
140: heat exchange unit 152: expander
154: refrigerant compressor 156: refrigerant cooler
160: first carburetor 170: second carburetor
180: booster compressor E1: first demand
E2: Second Demand L10: Recovery Line
L11: compression line L12: main supply line
L13: first low pressure fuel line L14: second low pressure fuel line
L15: fuel replenishment line L16: refrigerant circulation line
Q1: first measuring part V1: first control valve
V2: 2nd control valve

Claims (8)

An evaporation gas compressor for compressing the evaporation gas supplied from the storage tank;
a mixer for condensing the compressed boil-off gas by mixing it with liquefied gas supplied from the internal pump of the storage tank;
a pressurization pump that pressurizes the mixed fluid that has passed through the mixer according to fuel supply conditions of a first consumer;
a heat exchange unit that recovers cold heat from the mixed fluid passing through the pressure pump;
a first vaporizer that vaporizes the mixed fluid that has passed through the heat exchanger in accordance with the fuel supply conditions of the first consumer;
a supercooler for subcooling a part of the mixed fluid passing through the mixer by heat exchange with a refrigerant; and
A fuel supply system for a ship comprising a recovery line connecting the supercooler and the storage tank and recovering the mixed fluid that has passed through the supercooler into the storage tank. According to claim 1,
The evaporation gas compressor compresses the evaporation gas supplied from the storage tank to a low pressure according to the operating conditions of the mixer,
An evaporation gas cooling and heat recovery unit for cooling the evaporation gas compressed by the evaporation gas compressor by exchanging heat with the evaporation gas supplied from the storage tank;
A compression line for supplying the boil-off gas supplied from the storage tank to the boil-off gas compressor via the boil-off gas cold heat recovery unit;
A main supply line for supplying the boil-off gas compressed by the boil-off gas compressor to the mixer via the boil-off gas cold heat recovery unit and connecting the mixer, the pressure pump, the heat exchanger, the first vaporizer, and the first consumer Ship's fuel supply system. According to claim 2,
A first low-pressure fuel line branched from the rear end of the boil-off gas compressor of the main supply line and connected to a second consumer using a lower pressure fuel gas than the first consumer;
A first measurement unit provided in the main supply line and measuring the flow rate passing through the boil-off gas compressor;
A first control valve provided in the first low-pressure fuel line and opened so that at least a part of the boil-off gas compressed by the boil-off gas compressor is supplied to the second consumer when the measured flow rate exceeds a set fuel supply amount. Ship's fuel supply system further comprising. According to claim 2,
The main supply line is branched from the front end of the pressure pump and connected to a second consumer using low-pressure fuel gas through the heat exchange unit, and at least a part of the mixed fluid passing through the mixer is heated by the heat exchange unit. A second low-pressure fuel line to be supplied to two consumers;
A fuel supply system for a ship further comprising a second vaporizer provided in the second low-pressure fuel line and vaporizing the mixed fluid that has passed through the heat exchanger to a low pressure in accordance with the fuel supply conditions of the second consumer. According to claim 2,
A fuel replenishment line branched from the rear end of the boil-off gas compressor of the main supply line and connected to the rear end of the first carburetor of the main supply line;
A fuel supply system for a ship further comprising a booster compressor provided in the fuel replenishment line and compressing the boil-off gas compressed by the boil-off gas compressor in accordance with the fuel supply conditions of the first consumer. According to claim 2,
The boil-off gas compressor compresses to a high pressure in accordance with the fuel supply conditions of the first customer,
A second control valve provided at a rear end of the boil-off gas compressor in the main supply line and converting the pressure of the boil-off gas compressed by the boil-off gas compressor to suit the operating conditions of the mixer;
It is branched from the rear end of the boil-off gas compressor of the main supply line and connected to the rear end of the heat exchange part of the main supply line, and at least some of the boil-off gas compressed by the boil-off gas compressor to meet the fuel consumption of the first consumer. Ship's fuel supply system further comprising a fuel replenishment line for supplying to the first demand side. According to claim 1,
Further comprising a refrigerant circulation line for circulating the refrigerant,
An expander, a refrigerant compressor, and a refrigerant cooler are provided in the refrigerant circulation line to expand, compress, and cool the refrigerant,
The refrigerant expanded by the expander undergoes primary heat exchange with the mixed fluid flowing along the recovery line by the heat exchange unit, and then undergoes secondary heat exchange with the refrigerant that has passed through the refrigerant cooler to recover cold heat, followed by the refrigerant compressor, Ship's fuel supply system that circulates toward the expander through the refrigerant cooler and heat exchanger. According to claim 1,
The mixer is a fuel supply system for a ship, characterized in that the mixer is a recondenser or an in-line type mixer.

Images