JP2022186667A - Circuit for re-liquefying fluid and supplying re-liquefied fluid to consumption unit - Google Patents

Abstract

To execute control to prevent the pressure in the highest part of a tank from damaging the tank relating to a field of a vessel using, storing, and/or conveying liquefied natural gas and/or liquefied petroleum gas.SOLUTION: The present invention is related to a circuit (1) in which first fluid (4) stored in a first tank (2) and second fluid (8) stored in a second tank (6) flow. The circuit (1) includes at least one management pipe (20) for managing the state of the second fluid (8) intended for the second fluid (8) taken in a liquid state from the second tank (6) to pass and flow through. The circuit (1) includes a supply pipe (15) extending from a second pipe (16) to a consumption device (17) for supplying the first fluid (4) to the consumption device (17) that uses it as a fuel. The supply pipe (15) is configured so that the first fluid (4) in a liquid state passes and flows through it, and the supply pipe (15) includes at least one pump element (19) for increasing the pressure of the first fluid (4) in the supply pipe (15).SELECTED DRAWING: Figure 1

Description

The present invention relates to the field of ships that use, store and/or transport liquefied natural gas and/or liquefied petroleum gas, and more particularly liquefied natural gas and/or transported on such ships. Or belongs to the field of systems for controlling the condition of liquefied petroleum gas.

Such vessels customarily include tanks containing natural gas in liquid form and/or petroleum gas in liquid form. Such vessels may, for example, include a first tank for storing natural gas in liquid form and a second tank for storing petroleum gas in liquid form. On the one hand, such a vessel may transport a first petroleum gas contained in a first tank and a second petroleum gas contained in a second tank, the first petroleum gas being e.g. 2 Different from petroleum gas. That is, such vessels may transport a first fluid, which may be liquefied natural gas or liquefied petroleum gas, and a second fluid, different from the first fluid, which may be liquefied natural gas or liquefied petroleum gas. .

Natural gas is liquid at temperatures below −160° C. at atmospheric pressure, for example. Such tanks are never completely thermally insulated, which means that at least part of the natural gas evaporates within the tank. Such tanks therefore contain both liquid and gaseous natural gas, the gaseous natural gas, also called "BOG" or "boil-off gas", accumulating at the top of the tank. . The pressure at the top of this tank must be controlled so as not to damage the tank.

Petroleum gas generally has a boiling point between 0° C. and 50° C. at atmospheric pressure, depending on its composition. Also, petroleum gas tends to at least partially evaporate when stored in a tank, and the pressure at the top of the tank caused by the evaporated petroleum gas must also be controlled so as not to damage the tank.

Typically, such vessels are equipped with multiple systems for managing the condition of the first and second fluids in order to limit the evaporation of each such fluid at the top of the tank. . Such a management system is therefore arranged to liquefy the first fluid on the one hand and to liquefy the second fluid independently of the liquefaction of the first fluid on the other hand. Further, systems for managing either one of a plurality of fluids generally include compression elements for compressing the vaporized first fluid and/or the second fluid, increasing the pressure of said fluids by means of these compression elements. can be done. As a result, this type of management system is generally quite bulky and takes up considerable space either on the ship or around the docks. Also, these management systems are not suitable for supplying consuming devices that use either one of multiple fluids as fuel.

The present invention aims to reduce the volume occupied by the management system while supplying the first fluid and/or the second fluid to a consumer that uses the first fluid and/or the second fluid as fuel, and to reduce the volume of these two fluids. The goal is to reduce the space occupied by these compression elements in order to manage the state of More particularly, the present invention proposes a system for controlling the state of the vaporized first fluid, which system also makes it possible to cool the second fluid in its liquid state, whereby the vaporized second fluid It is also possible to send a portion of the first fluid in liquid state as fuel to the consumer in a decreasing amount.

The present invention primarily relates to a circuit through which a first fluid contained in a first tank and a second fluid contained in a second tank can flow, the first fluid having a boiling point lower than the boiling point of the second fluid wherein the circuit includes at least a first pipe extending from the first tank to the heat exchange element, a first fluid taken from the first tank in gaseous state being intended to flow through the first pipe and heat exchanging The element is configured to condense the first fluid, the circuit includes a second pipe extending from the heat exchange element to the first tank, the first fluid in liquid state and/or two-phase state flowing through the second pipe. and the circuit includes at least one control line for controlling the condition of the second fluid, through which the second fluid taken in liquid form from the second tank is intended to flow, the circuit comprising at least including a supply pipe extending from the second pipe to the consuming device for supplying the first fluid to the consuming device for use as fuel, the supply pipe being configured to flow at least the first fluid in liquid state therethrough; The tube is characterized by at least one pumping element for increasing the pressure of the first fluid in at least the supply tube.

The circuit controls on the one hand at least the pressure and temperature, more generally the state, of the first fluid contained in the first tank and the second fluid contained in the second tank, and on the other hand at least Note that the first fluid is supplied as fuel. The consuming unit can be, for example, a propulsion engine or an auxiliary engine onboard the ship in which the circuit according to the invention and the first and second tanks are installed.

The pump element in particular makes it possible to increase the pressure of at least the first fluid flowing in liquid state through the supply line to the consumption unit. The present invention takes advantage of the fact that the pressure of the first fluid is high as it passes through the first pipe, and this high pressure on the one hand liquefies the first fluid to create the pressure in the first tank, It is also used accordingly to manage the pressure in the second tank and, on the other hand, to supply the consumer. The pressure required to supply the consumer is therefore a combination of the pressure prevailing in the first line and the pressure supplied by the pump element. This clever combination allows the use of less complex, cheaper and more reliable pumping elements.

Furthermore, using the first fluid as fuel has the advantage of reducing the energy consumption required for thermal management of the first fluid contained in the first tank. This reduction can represent an energy savings of up to 30% compared to a circuit that does not include such plumbing supplying consumers.

The first and second fluids are, for example, petroleum gas stored in liquid form in tanks, the first fluid comprising, for example, 92% propane and 8% butane, having a boiling point of −47° C. at atmospheric pressure. That is, the first fluid is liquid when its temperature is below −47° C. at atmospheric pressure, and the second fluid consists, for example, of about 100% butane and has a boiling point of 0° C. at atmospheric pressure. have, ie, the second fluid is liquid if its temperature is below 0° C. at atmospheric pressure.

According to another embodiment of the invention, the first fluid is, for example, mostly natural gas, such as methane, and has a boiling point of about -160°C at atmospheric pressure.

According to another embodiment of the invention, the first fluid consists for example of 100% ethane and has an evaporation temperature of −89° C. and the second fluid comprises a mixture of 92% propane and 8% butane. It consists of liquefied petroleum gas and has an evaporation temperature of -47°C.

According to another embodiment of the invention, the first fluid consists for example of 100% ethane and has an evaporation temperature of -89°C and the second fluid consists of 100% ammonia with an evaporation temperature of -33°C. Become.

According to another embodiment of the invention, the first fluid consists for example of 100% propane and has an evaporation temperature of -42°C and the second fluid consists of 100% ammonia with an evaporation temperature of -33°C. Become.

The above temperatures are measured at atmospheric pressure.

Furthermore, "the supply tube is configured to allow at least the first fluid in liquid state to flow therethrough" means that in the first embodiment of the invention, only the first fluid flows through the supply tube. Alternatively, in a second embodiment of the invention, it is meant that the supply tube carries a first fluid and at least one other fluid, such as a second fluid.

According to another optional feature of the invention, the circuit comprises at least one cooling pipe extending from the second pipe to the first pipe intended for the flow of the first fluid, the first pipe At least a compression element and a second compression element are included, and the cooling pipe is connected to the first pipe between the first compression element and the second compression element.

According to another optional feature of the invention, the circuit includes at least one cooling unit for cooling the second fluid in liquid state flowing through the management piping for managing the condition of the second fluid, the cooling unit The cold produced is caused by evaporation (boil-off) of the first fluid flowing through at least one cooling pipe extending from the second pipe to the first pipe and through which the first fluid is intended to flow.

The second fluid flowing through the management pipe is cooled by the cooling unit, and the temperature of the second fluid flowing through the management pipe downstream of the cooling unit is lower than the temperature of the first fluid flowing through the cooling pipe downstream of the cooling unit. This has the effect of reducing the temperature of the second fluid contained in the second tank, thereby limiting the evaporation of the second fluid present in the second tank.

The cold air used to lower the temperature of the second fluid flowing through the management pipes comes from the evaporation of a portion of the first fluid flowing through the cooling pipes. More specifically, a portion of this first fluid is expanded, i.e. a portion of this first fluid is depressurized so that the heat exchange between the first and second fluids causes the second The temperature of the two fluids is lowered.

According to another optional feature of the invention, the cooling unit includes at least a heat exchanger and an expansion element, the heat exchanger providing heat transfer between the first fluid flowing through the cooling pipes and the second fluid flowing through the management pipes. exchange energy.

More specifically, the first fluid flowing through the cooling tubes is expanded by an expansion element before flowing through the heat exchanger. As the second fluid flowing through the management pipe passes through the heat exchanger, it transfers thermal energy to the expanded first fluid flowing through the cooling tubes and also passing through the heat exchanger. Therefore, the second fluid flowing through the management pipe is cooled downstream of the cooling unit to a temperature close to the temperature of the first fluid flowing through the cooling pipe.

In other words, the first fluid flowing through the cooling pipes and passing through the heat exchanger is warmed and vaporized within the heat exchanger by gaining thermal energy from the second fluid flowing through the management pipes. The warmed and vaporized first fluid is then sucked by one of the plurality of compression elements attached to the first pipe.

Furthermore, it is inside the heat exchanger that the temperature of the second fluid flowing through the management pipe decreases. Specifically, heat energy is transferred from the second fluid flowing through the management pipe to the first fluid flowing through the cooling pipe. , approaches the temperature of the first fluid flowing through the cooling pipe. It should be noted that the temperature of the second fluid flowing through the management pipe will drop during the exchange of thermal energy taking place in the heat exchanger.

According to another optional feature of the invention, the heat exchanger includes at least a first passageway forming a cooling pipe and a second passageway forming a management pipe, the expansion element comprising the first passageway and the second passageway. Placed between pipes.

Note that in this configuration, the first fluid flowing through the cooling tubes is expanded by the expansion element before the first fluid flows through the first passage of the heat exchanger.

According to another optional feature of the invention, the circuit includes at least one pipe extending from the second pipe to the first pipe through which the first fluid flows, the circuit comprising the first pipe flowing through the second pipe. At least one cooling device is included for cooling a fluid, the cold air produced by the cooling device resulting from evaporation of the first fluid flowing through the pipe.

The first fluid flowing through the second pipe is cooled by the cooling device, and the temperature of the first fluid flowing through the second pipe downstream of the cooling device is lower than the temperature of the first fluid flowing through the pipe downstream of the cooling device.

The cold air used to reduce the temperature of the first fluid flowing through the second pipe comes from evaporation of a portion of the first fluid flowing through the pipe. More specifically, a portion of this first fluid is expanded, i.e. a portion of this first fluid is depressurized so that the first fluid flows through the second pipe with this first fluid. temperature is lowered.

According to another optional feature of the invention, the supply pipe is connected to the second pipe at a branch point arranged on the second pipe between the heat exchange element and the cooling device. That is, the branching point between the second pipe and the supply pipe is arranged upstream of the cooling device and downstream of the heat exchange element.

According to another optional feature of the invention, the circuit includes at least one phase separating element for the first fluid arranged on the second pipe, the first fluid flowing from the phase separating element to the second pipe. to the first tank and the circuit includes a gas line extending from the phase separation element to the second line. Note that the flow diversion point is located in a portion of the second piping downstream of the phase separation element.

According to another optional feature of the invention, the feed pipe is connected to the second pipe at a branching point arranged on the second pipe between the phase separation element and the cooling device. Therefore, the first fluid flowing through the feed pipe is caused by the accumulation of the first fluid in liquid state in the phase separation element.

According to another optional feature of the invention, the supply pipe extends from the cooling pipe to the consumer, and the junction of the supply pipe and the cooling pipe is arranged between the cooling device and the cooling unit. Note that the first fluid is cooled by the cooling device before flowing through the supply pipe.

According to another optional feature of the invention, the supply pipe extends from the cooling pipe to the consumer, and the junction of the supply pipe and the cooling pipe is arranged between the expansion element of the cooling unit and the cooling device.

According to another optional feature of the invention, the circuit includes a control valve for controlling the flow rate of the first fluid through the supply pipe. That is, the control valve is attached to the supply line upstream of the pump element.

According to another optional feature of the invention, the circuit includes a carrier pipe extending between the management pipe and the supply pipe. Thus, the carrier pipe will fluidly connect the management pipe to the supply pipe.

Further features, details and advantages of the invention will be obtained on the one hand from reading the following description and on the other hand from some embodiments given as non-limiting examples with reference to the accompanying drawings. will be clearer. In the drawing:

1 schematically represents a circuit according to a first embodiment; 2 schematically represents a circuit according to a second embodiment; 3 schematically represents a circuit according to a third embodiment;

Features, variations and different embodiments of the invention may be associated with each other in various combinations unless contradictory or mutually exclusive. Specifically, a variation of the invention that includes, apart from other features described, only a selected one of the plurality of features described below, wherein the selected feature provides a technical advantage, and/or if sufficient to differentiate the present invention from the prior art.

Furthermore, the terms "upstream" and "downstream" used in the description below refer to the direction of circulation of the first and/or second fluids in a circuit through which the first and second fluids can flow. .

FIG. 1 shows a circuit 1 containing at least a first fluid 4 and a second fluid 8 , a first tank 2 containing the first fluid 4 and a second tank 6 containing the second fluid 8 . The first tank 2 , the second tank 6 and/or the circuit 1 can be installed, for example, on a ship that transports the first fluid 4 and the second fluid 8 .

The first fluid 4 has a boiling point lower than that of the second fluid 8 and these two temperatures are measured at the same pressure. The first fluid 4 is for example natural gas such as methane and has a boiling point of about -160°C, ie the first fluid 4 is liquid at temperatures below -160°C at atmospheric pressure. The second fluid 8 is petroleum gas, for example propane, butane, or a mixture of propane and butane, and has a boiling point between 0°C and -51°C at atmospheric pressure. However, the first fluid 4 can also be a petroleum gas such as propane, butane, or a mixture of propane and butane, so long as the first fluid 4 has a boiling point lower than that of the second fluid 8 .

According to the example shown herein, the first fluid 4 and the second fluid 8 are petroleum gas, the first fluid 4 comprising, for example, about 92% propane and about 8% butane, at atmospheric pressure - A mixture having a boiling point of 47° C., the second fluid 8 consists, for example, of about 100% butane and has a boiling point of 0° C. at atmospheric pressure.

According to a first alternative of the invention, the first fluid 4 is ethane and has a boiling point of -89°C and the second fluid 8 is a liquefied petroleum gas comprising a mixture of propane and butane and is -47°C. It has a boiling point of °C.

According to a second alternative of the invention, the first fluid 4 is ethane and has an evaporation temperature of -89°C and the second fluid 8 is ammonia and has a boiling point of -33°C.

According to a third alternative of the invention, the first fluid 4 is propane and has a boiling point of -42°C and the second fluid 8 is ammonia and has a boiling point of -33°C.

The first tank 2 and the second tank 6 are designed to store the first fluid 4 and the second fluid 8 in liquid form at temperatures below their respective boiling points at atmospheric pressure. To this end, the tanks 2 and 6 each have at least a sealing membrane in contact with one or the other of these fluids and a sealing membrane surrounding the sealing membrane to keep one or the other of the fluids at a temperature below its boiling point. consists of an insulating barrier that helps

Advantageously, each of the tanks 2, 6 surrounds a primary layer consisting of a primary sealing membrane in contact with one of these fluids and a primary insulating barrier surrounding the primary sealing membrane, and It has a secondary layer comprised of a secondary sealing membrane in contact with the primary insulating barrier and a secondary insulating barrier surrounding the secondary sealing membrane.

The first fluid 4 is mainly liquid under atmospheric pressure and stored in the first tank 2 . However, part of the first fluid 4 evaporates and forms a cover at the top 10 of the first tank 2, where the first fluid 4 is therefore present in gaseous form.

Similarly, the second fluid 8 is mainly liquid under atmospheric pressure and stored in the second tank 6 . However, part of the second fluid 8 evaporates and forms a cover at the top 11 of the second tank 6, where the second fluid 8 is therefore present in gaseous form.

The circuit 1 is arranged to re-liquefy at least part of the gaseous first fluid 4 present in the top 10 of the first tank 2 and to supply the first fluid to a consumer using the first fluid 4 as fuel. 4. Towards this end, the circuit 1 comprises a first pipe 12 through which the first fluid 4 flows from the first tank 2 to the plurality of compression elements 14, and a first pipe 12 through which the first fluid 4 is in a liquid state and/or in a two-phase state. and a second line 16 extending from the first line 12 to the first tank 2 through which the first line 12 flows to the first tank 2 . Furthermore, the circuit 1 includes a cooling tube 18 extending from the second line 16 to the first line 12 through which the first fluid 4 flows from the second line 16 to the first line 12 .

According to the invention, the circuit 1 comprises a supply pipe 15 for supplying the first fluid to a consumer 17 using it as fuel, which supply pipe 15 extends from the second pipe 16 to the consumer 17 and which is in liquid state. A first fluid 4 flows through this supply tube 15 , which includes at least one pumping element 19 for increasing the pressure of the first fluid 4 within the supply tube 15 . It should be noted that part of the first fluid 4 flowing through the second pipe 16 is intended to flow through the supply pipe 15 for use as fuel for the consumer 17 . Furthermore, the first fluid 4 flowing through the supply pipe is in a liquid state and the pump element 19 increases the pressure of the first fluid 4 flowing through the supply pipe 15 to the consumer 17 .

A more detailed description of supply pipe 15 is provided further below, and more particularly after first pipe 12 , second pipe 16 , cooling unit 24 , cooling pipe 18 , and management pipe 20 .

Furthermore, the circuit 1 further comprises at least one control line 20 for controlling the condition of the second fluid, through which control line 20 at least part of the second fluid 8 flows from the second tank 6 to the second tank. 6 to the liquid outlet 22 for the second fluid 8 . Specifically, the liquid outlet 22 sprays the cooled second fluid 8 into the second tank 6 , specifically to cool the second fluid 8 present at the top 11 of the second tank 6 . make it possible to By reducing the temperature of the second fluid 8 present at the top 11 of the second tank 6 , the pressure exerted by the vaporized second fluid 8 present at said top 11 of the second tank 6 can be reduced. According to the embodiment shown herein in FIG. 1, the liquid outlet 22 is in the form of a spray bar that facilitates distribution of the sprayed second fluid 8 onto the top 11 of the second tank 6. .

The management system 1 comprises a cooling unit 24 for cooling the liquid state second fluid 8 flowing through the management pipe 20 , the cold generated by the cooling unit 24 being the result of the evaporation of the first fluid 4 flowing through the cooling pipes 18 . . Note that the first fluid 4 is at a sufficiently low temperature if the first fluid 4 flows through the cooling pipe 18 and the cooling unit 24 to cool the second fluid 8 flowing through the management pipe 20. . In this case the second fluid 8 transfers thermal energy to the first fluid 4 .

A more detailed description of the second piping 16, the cooling unit 24, the cooling pipes 18, the management piping 20, and the supply pipes 15 of the circuit 1 is provided after the description of the first piping 12 below, with particular reference to FIG. .

The first pipe 12 extends from the interior of the first tank 2, more specifically to the top 10 of the first tank 2, where the first fluid 4 in gaseous phase is present. It includes an open gas inlet 26 . Thus, the gaseous first fluid 4 present at the top 10 of the first tank 2 is in direct contact with the gas inlet 26 of the first pipe 12, resulting in a plurality of compressions of the gaseous first fluid 4. It can be inhaled by element 14 .

The first fluid 4 in gaseous state moves from the top 10 of the first tank 2 through the first pipe 12 to the plurality of compression elements 14 under the influence of suction created by the plurality of compression elements 14 . More particularly, the plurality of compression elements 14 are configured to increase the pressure of the first gaseous fluid 4 before the first gaseous fluid 4 is delivered to the consumer.

As shown in FIG. 1, the plurality of compression elements 14 includes a first compression element 14a, a second compression element 14b, and a third compression element 14c, on the first pipe 12 and within said first pipe. They are arranged in this order in the direction of circulation of one fluid 4 . The plurality of compression elements 14 includes a first portion 28 of the first pipe 12 extending between the gas inlet 26 and the first compression element 14a and a first pipe extending between the first compression element 14a and the second compression element 14b. 12, a third portion 32 of the first pipe 12 extending between the second compression element 14b and the third compression element 14c, and a first pipe 16 extending between the third compression element 14c and the second pipe 16. It helps define the fourth portion 34 of the tubing 12 .

The pressure of the gaseous first fluid 4 increases as it flows through the plurality of compression elements 14 and through the first pipe 12, the first fluid 4 being at atmospheric pressure in the first portion 28 and about A pressure of 24 bar is reached.

As shown in FIG. 1 , the coolant circulation system 36 includes at least one heat exchange element for heat exchange between the coolant flowing through the circulation system 36 and the gaseous first fluid 4 flowing through the first pipe 12 . 38. This heat exchange element 38 separates the first pipe 12 from the second pipe 16 . More specifically, the heat exchange element 38 is arranged downstream of the fourth section 34 of the first pipe 12 .

A heat exchange element 38 exchanges thermal energy between the coolant and the first fluid 4 . The coolant may be a heat transfer fluid and/or water, and the circulation system 36 may be installed, for example, on a vessel and directly connected to the body of water in which the vessel is navigating.

Advantageously, the circulation system 36 comprises a first heat exchange element 40 attached to the second portion 30 of the first pipe 12, a second heat exchange element 42 attached to the third portion 32 of the first pipe 12, and a and a third heat exchange element 38 attached to a fourth portion 34 of the first pipe 12 , each of the heat exchange elements 38 , 40 , 42 , each of which separates the first fluid 4 in gaseous state and the cooling liquid flowing through the first pipe 12 . exchange heat energy between Alternating compression elements 14 and heat exchange elements 38, 40, 42 arranged along the first pipe 12 reduce the temperature of the first fluid 4 after each stage of compression performed by the compression elements. Note that you can.

In the example shown herein in FIG. 1, when the first fluid 4 passes through multiple compression elements 14, the pressure and temperature of the fluid increases. To prevent this temperature from becoming too high, the first fluid 4 exchanges thermal energy with the coolant using first, second and third heat exchange elements 40,42,38. For example, the temperature of the first fluid 4 flowing through the second portion 30 downstream of the first heat exchange element 40 is about 7° C., and the temperature of the first fluid 4 flowing through the third portion 32 downstream of the second heat exchange element 42 is about 7° C. The temperature is about 40°C and the temperature of the first fluid 4 flowing through the fourth portion 34 downstream of the third heat exchange element 38 is above 43°C.

Furthermore, the boiling point of the fluid also changes according to the pressure to which the fluid is subjected. The first fluid 4, which can be, for example, a mixture of about 92% propane and about 8% butane, has a boiling point of about 43°C when subjected to a pressure of about 24 bar. Thus, the first fluid 4 is in a gaseous state in the fourth portion 34 upstream of the third heat exchange element 38 and is in a liquid state or liquid state while passing through the third heat exchange element 38 by exchanging thermal energy with the coolant. It will transition to a two-phase state and flow through the second pipe 16 downstream of the third heat exchange element 38 in a liquid or two-phase state. Therefore, the first fluid 4 flows downstream of the third heat exchange element 38 in the second pipe 16 in a liquid state or a two-phase state.

Furthermore, "two-phase state" means a state in which a portion of the first fluid 4 is in a liquid state and another portion of the first fluid 4 is in a gaseous state.

Before discussing the cooling unit 24, the cooling pipes 18, the management pipes 20 and the supply pipes 15 in more detail, the second pipes 16 of the circuit 1 will now be described in more detail, particularly with reference to FIG.

The first fluid 4 flows from the first pipe 12 through the second pipe 16 and more particularly from the third heat exchange element 38 to the first tank 2 .

As shown in FIG. 1, the management system 1 includes a phase separation device 44 for the first fluid 4 arranged on the second pipe 16 . The phase separator 44 is configured to separate multiple phases present in the first fluid 4 flowing through the second conduit 16 . That is, the phase separation device 44 is configured such that the first fluid 4 in liquid state is separated from the first fluid 4 in gaseous state. The liquid state first fluid 4 separated in the phase separator 44 flows to the second pipe 16 .

The circuit 1 includes a gas line 46 through which the first fluid 4 flows from the phase separation device 44 to the second line 16 .

As shown in FIG. 1 , the management system 1 connects the first pipe 12 with the second pipe 16 and provides at least one pipe 48 through which the first fluid 4 flows from the second pipe 16 to the first pipe 12 . include. The management system 1 includes at least one cooling device 50 for cooling the first fluid 4 flowing through the second pipe 16 , the cold produced by the cooling device 50 resulting from evaporation of the first fluid 4 flowing through the pipe 48 .

An intersection 52 is formed between the pipe 48 and the second pipe 16 , and the first fluid 4 flows through the second pipe 16 to the first tank 2 or through the pipe 48 to the first pipe 12 at this intersection. Able to flow either way, the cooling device 50 is configured such that evaporation of the first fluid 4 flowing through the pipe 48 reduces the temperature of the first fluid 4 flowing through the second line 16 .

Further, as shown in FIG. 1, gas pipe 46 is connected to second pipe 16 downstream of intersection 52 of second pipe 16 and pipe 48 . As the first fluid 4 in gaseous state flowing in the gas pipe 46 mixes with the first fluid 4 in liquid state flowing in the second pipe 16 downstream of the intersection 52 , the first fluid 4 flows in the second pipe 16 at the intersection 52 and the cooling device 50 in two phases.

More specifically, the cooling device 50 includes at least a heat exchanger 54 and an expansion device 56, the heat exchanger 54 includes a first passage 58 forming the second pipe 16 and a second passage 60 forming the pipe 48, The expansion device 56 is positioned on the pipe 48 upstream of the second passageway 60 . The heat exchanger 54 is configured to exchange heat between the first fluid 4 flowing through the second conduit 16 and the first fluid 4 flowing through the pipe 48 .

With this configuration, the heat exchanger 54 exchanges thermal energy between the first fluid 4 flowing through the second pipe 16 and the first fluid 4 flowing through the pipe 48 , and the first fluid 4 flowing through the second pipe 16 . and the first fluid 4 flowing through the pipe 48 specifically takes place in the first passage 58 and the second passage 60 of the heat exchanger 54 . Due to the thermal energy exchanged between the first fluid 4 flowing through the second pipe 16 and the first fluid 4 flowing through the pipe 48, the temperature of the first fluid 4 flowing through the second pipe 16 decreases, causing the second pipe 16 to The flowing first fluid 4 transfers thermal energy to the first fluid 4 flowing through pipe 48 .

This transfer of thermal energy is achieved thanks to the presence of the expansion device 56 which lowers the pressure of the first fluid 4 flowing through the pipe 48 and facilitates its change of state.

The temperature drop between the first fluid 4 flowing upstream of the first passage 58 of the second pipe 16 and the first fluid 4 flowing downstream of the first passage 58 of the second pipe 16 is at least 20°C. Advantageously, this temperature difference is between 25°C and 35°C.

Due to the decrease in temperature of the first fluid 4 flowing through the second pipe 16, the first fluid 4 changes from a two-phase state to a liquid state. Accordingly, the first fluid 4 flowing in the second line 16 downstream of the first passage 58 of the heat exchanger 54 is in a liquid state, for example having a temperature of about 14° C. and a pressure of about 24 bar.

As shown in FIG. 1, the expansion element 56 of the cooling device 50 is attached to the pipe 48 upstream of the second passageway 60 . In other words, the first fluid 4 in the liquid state supplied to the second passage 60 expands before reaching the second passage 60, that is, the pressure decreases and the state of the first fluid 4 changes, Note the resulting transition from a two-phase state to a gaseous state within the second passageway 60 . For example, the first fluid 4 may be expanded to a pressure of about 3 bar so that the first fluid 4 expands from a pressure of about 24 bar upstream of the expansion element 56 to a pressure of 3 bar between the expansion element 56 and the first pipe 12 . can change to a pressure of

The pressure difference between the gaseous first fluid 4 flowing through the second passageway 60 and the liquid or two-phase first fluid 4 flowing through the first passageway 58 , and the resulting temperature difference, causes the first fluid 4 to flow through the first passageway 58 . The liquid or two-phase first fluid 4 is cooled and the two-phase first fluid 4 entering the second passageway 60 evaporates.

As shown in FIG. 1 , the expanded gaseous first fluid 4 flowing downstream of the second passage 60 then reaches the first pipe 12 . Advantageously, the pipe 48 is connected to the first pipe 12 at its second portion 30, more particularly between the first heat exchange element 40 and the second compression element 14b. Accordingly, the expanded gaseous first fluid 4 is mixed with the first fluid 4 from the first heat exchange element 40 and this mixture is sucked into the third portion 32 of the first pipe 12 by the second compression element 14b. be.

As shown in FIG. 1, the management system 1 includes a phase separator 62 for the first fluid 4 attached to the second pipe 16 downstream of the cooling device 50, the management system 1 comprising the phase separator 62 and the first It includes a return line 64 extending between the lines 12 through which the gaseous first fluid 4 flows.

Separator 62 includes a phase separator main section 66 and an expansion element 68 positioned on second line 16 upstream of phase separator main section 66 . The expansion element 68 allows the first fluid 4 flowing to the phase separator main section 66 to be at substantially the same pressure as the first fluid 4 contained in the first tank 2, i.e. atmospheric pressure.

More specifically, the first fluid 4 in liquid state flowing through the second pipe 16 to the first tank 2 increases the pressure of the first fluid 4 existing in the second pipe to the pressure of the first fluid 4 contained in the first tank 2 . Note that it expands before reaching the first tank 2 to match the pressure of , ie its pressure drops. Expansion of the first fluid 4 by the expansion element 68 changes the state of the first fluid 4 so that it changes from a liquid state to a two-phase state in which part of the first fluid 4 is in a liquid state and another part is in a gaseous state. Move to Moreover, the temperature of the first fluid 4 also decreases due to this decrease in pressure. For example, the first fluid 4 may be expanded to a pressure of approximately 1.2 bar so that the first fluid 4 expands from a pressure of approximately 24 bar upstream of the expansion element 68 to a pressure of approximately 1.2 bar downstream of the expansion element 68 . and the first fluid 4 has a temperature of about -50°C.

The first fluid 4 then flows to the phase separator main part 66, where the first fluid 4 is in a liquid state and/or a two-phase state depending on its exact temperature. The phase separator main section 66 is configured to separate multiple phases present in the first fluid 4 flowing from the expansion element 68 to the first tank 2 . That is, the phase separator main part 66 is configured to separate the first fluid 4 in the liquid state from the first fluid 4 in the gaseous state. Then, the first fluid 4 in the liquid state separated by the main part 66 of the phase separator flows into the first tank 2, and the first fluid 4 in the gaseous state passes through the return pipe 64 to the first portion of the first pipe 12. Go to 28.

Advantageously, the second pipe 16 opens into the first tank 2, in particular to a fluid outlet 65 at the bottom of the first tank 2, so that the first fluid 4 in its liquid state reaches the main phase separator. It flows from the part 66 through the second pipe 16 to the bottom of the first tank 2 . According to an alternative, the second pipe 16 opens at the top 10 of the first tank 2 and the first fluid 4 in liquid state is for example sprayed at the top 10 of the first tank 2 so that the first The gaseous first fluid 4 present at the top 10 of the tank 2 is cooled.

In the example shown here in FIG. 1, the management system 1 is arranged on the return pipe 64 to cause the first fluid 4, for example in gaseous state, to flow through the return pipe 64 to a pressure of 1.2 bar. an expansion block 70 for expanding the first fluid 4 configured to change from pressure to atmospheric pressure.

The management system 1 further includes an exhaust pipe 72 connected to the return pipe 64 downstream of the expansion block 70 and opening to the environment outside the management system 1 .

The management system 1 includes a flow control device for controlling the flow rate of the first fluid 4 in a gaseous state, which is arranged on the discharge pipe 72 to control the flow rate of the first fluid 4 discharged to the external environment of the management system 1. A control valve 74 is included.

Before discussing supply pipe 15, cooling pipe 18, management pipe 20, and cooling unit 24 will now be described in more detail, particularly with reference to FIG.

As shown in FIG. 1, cooling pipe 18 extends between second pipe 16 and first pipe 12 . Therefore, the first fluid 4 flows from the second pipe 16 to the first pipe 12 through the cooling pipe 18 .

According to one aspect of the invention, the cooling pipe 18 is connected to the second pipe 16 downstream of the cooling device 50 . The first fluid 4 flowing through the cooling pipe 18 from the second pipe 16 to the first pipe 12 passes through at least a portion of the pipe 48 and mixes with the first fluid 4 flowing in the pipe 48 downstream of the cooling device 50 . be done. Therefore, the first fluid 4 from the cooling pipe 18 is injected between the first heat exchange element 40 and the second compression element 14b, and the first fluid 4 flowing through the second portion 30 of the first pipe 12 and will be mixed.

According to the present invention, as shown in FIG. 1, the management system 1 comprises management piping 20 for managing the condition of the second fluid 8, specifically its pressure and/or temperature, which in liquid state A second fluid 8 taken from the second tank 6 is intended to flow through this management line 20 . Towards this end, the management line 20 includes a liquid inlet 76 located at the bottom of the second tank 6 , for example in contact with the second fluid 8 contained in the second tank 6 in liquid state.

According to one embodiment of the invention, the management system 1 includes at least one pump element 78 arranged on the management piping 20 upstream of the cooling unit 24 . The pumping element 78 is configured to cause the second fluid 8 in liquid state to flow through the management line 20 . To this end, a pump element 78 is attached to the liquid inlet 76 . In other words, the pump element 78 is immersed in the second fluid 8 in liquid state contained in the second tank 6 . However, the pumping element 78 can be mounted anywhere on the control line 20 as long as it pumps the second fluid 8 in its liquid state through the control line 20 .

The pumping element 78 increases the pressure of the liquid state second fluid 8 flowing through the management line 20 . For example, the second fluid 8 in liquid state flowing downstream of the pump element 78 has a pressure of about 4 bar, so that the pump element 78 reduces the pressure of the second fluid 8 in liquid state to a large pressure upstream of the pump element 78 . Change from atmospheric pressure to a pressure of about 4 bar downstream of the pump element 78 .

As shown in FIG. 1 , the management line 20 includes a liquid outlet 22 through which the second fluid 8 in liquid state flows through the management line 20 to the liquid outlet 22 . According to one embodiment, the liquid outlet 22 may comprise a spray element capable of spraying the second fluid 8 in liquid form from the management pipe 20 at the top 11 of the second tank 6 .

According to the invention, the management system 1 comprises a cooling unit 24 for cooling the second fluid 8 flowing through the management pipe 20 , the cold produced by the cooling unit 24 being generated by evaporation of the first fluid 4 flowing through the cooling pipe 18 . occur. Thus, the management line 20 includes a first portion 80 upstream of the cooling unit 24 and a second portion 82 downstream of the cooling unit 24 . Accordingly, the liquid state second fluid 8 flowing through the second portion 82 of the management pipe 20 has a temperature below the temperature of the liquid state second fluid 8 flowing through the first portion 80 of the management pipe 20 .

More specifically, as shown in FIG. 1 , the cooling unit 24 includes at least a heat exchanger 84 and an expansion element 86 attached to the cooling tubes 18 upstream of the heat exchanger 84 . are configured to exchange heat between the first fluid 4 flowing through the cooling pipe 18 and the second fluid 8 flowing through the management pipe 20 . Note that the heat exchangers 84 are attached to both the cooling pipes 18 and the management pipes 20 such that the first fluid 4 and the second fluid 8 pass through the heat exchangers 84 .

Towards this end, the heat exchanger 84 includes at least a first passageway 88 forming the cooling pipe 18 and a second passageway 90 forming the management pipe 20, with an expansion element 86 upstream of the first passageway 88. placed. The first fluid 4 flowing through the cooling pipe 18 passes through the heat exchanger 84 through the first passageway 88 and the second fluid 8 flowing through the management pipe 20 passes through the heat exchanger 84 through the second passageway 90 . Constructed in this way, the heat exchanger 84 exchanges thermal energy between the first fluid 4 flowing through the cooling pipe 18 and the second fluid 8 flowing through the management pipe 20 , and heats the first fluid 4 flowing through the cooling pipe 18 . The exchange of thermal energy between the second fluid 8 flowing through the management pipe 20 specifically takes place in the first passage 88 and the second passage 90 of the heat exchanger 84 . The thermal energy exchanged between the first fluid 4 and the second fluid 8 reduces the temperature of the second fluid 8 and the second fluid 8 transfers thermal energy to the first fluid 4 .

Furthermore, this thermal energy transfer is achieved thanks to the presence of the expansion element 86 which lowers the pressure of the first fluid 4 flowing through the cooling tube 18 and facilitates its change of state.

As shown in FIG. 1, expansion element 86 of cooling unit 24 is attached to cooling tube 18 upstream of first passage 88 . In other words, it should be noted that the liquid state first fluid 4 supplied to the first passageway 88 expands before reaching the first passageway 88; sea bream. This expansion causes the state of the first fluid 4 to change, transitioning from a two-phase state to a gaseous state in the second passage 90 . Therefore, the first fluid 4 is expanded to a pressure of about 3 bar, causing the first fluid 4 to go from a pressure of about 24 bar upstream of the expansion element 86 to a pressure of 3 bar downstream of the expansion element 86. Note that it can change.

A decrease in the pressure of the first fluid 4 through the expansion element 86 changes the state of the first fluid 4 and concurrently decreases its temperature. For example, first fluid 4 has a temperature of approximately 14° C. upstream of expansion element 86 and a temperature of approximately −30° C. between expansion element 86 and first passage 88 of heat exchanger 84 .

Advantageously, the temperature difference between the first fluid 4 flowing through the first passageway 88 and the second fluid 8 in liquid state flowing through the second passageway 90 causes the second fluid 8 in liquid state flowing through the second passageway 90 to Cooled, the two-phase first fluid 4 entering the first passageway 88 evaporates. Here, the second fluid 8 flowing through the second passageway 90 transfers thermal energy to the first fluid 4 flowing through the first passageway 88 , increasing the temperature of the first fluid 4 as it passes through the first passageway 88 . rises, thereby changing its state from a two-phase state to a gaseous state.

For example, the temperature of the second fluid 8 in liquid state is about 0° C. in the first portion 80 of the management pipe 20, i.e. upstream of the second passage 90 of the heat exchanger 84, and in the second portion 82 of the management pipe 20, i.e. Downstream of the second passage 90 is about -10°C.

Furthermore, the first fluid 4 flowing through the cooling tube 18 upstream of the expansion element 86 is in a liquid state and the first fluid 4 flowing through the cooling tube 18 between the expansion element 86 and the heat exchanger 84 is in a two-phase state, The first fluid 4 flowing through the cooling tube 18 is in a gaseous state within and downstream of the heat exchanger 84 . For example, the temperature of the first fluid 4 flowing through the cooling tube 18 upstream of the expansion element 86 is approximately 14° C., and the temperature of the first fluid 4 flowing through the cooling tube 18 between the expansion element 86 and the heat exchanger 84 is approximately It is -30°C, and the temperature of the first fluid 4 flowing downstream of the heat exchanger 84 is about -3°C.

Advantageously, expansion element 86, expansion device 56 and first compression element 14a are configured to bring first fluid 4 to the same pressure. The first compression element 14a will thus increase the pressure of the first fluid 4 flowing through the first pipe 12 to a pressure of, for example, 3 bar. The expansion element 86 and the expansion device 56 cause the pressure of the first fluid 4 flowing through the cooling pipe 18 and the first fluid 4 flowing through the pipe 48 to be the same as the pressure of the first fluid 4 flowing through the second portion 30 of the first pipe 12 . pressure, ie to a pressure of, for example, 3 bar. Thus, the gaseous first fluid 4 flowing through the pipe 48 downstream of the cooling device 50 is at a pressure of, for example, 3 bar, and the gaseous first fluid 4 flowing through the cooling pipe 18 downstream of the heat exchanger 84 is also at 3 bar. is the pressure of

The supply tube 15 will now be described in more detail with particular reference to FIG.

As a reminder, the supply pipe 15 extends between the second pipe 16 and the consumer 17 using the first fluid 4 as fuel, so that the first fluid is consumed from the second pipe 16 through the supply pipe 15. It flows to device 17 . A pumping element 19 attached to the supply tube 15 is for example arranged to cause the first fluid 4 to flow through the supply tube 15 to the consumer 17 .

According to the invention, as shown in FIG. Connected. That is, the supply pipe 15 is connected to the second pipe 16 between the third heat exchange element 38 and the cooling device 50 . It should be noted that in this arrangement the first fluid 4 flowing through the supply pipe towards the consumer 17 is in liquid form.

Furthermore, the first fluid 4 flows through the second pipe 16 between the third heat exchange element 38 and the cooling device 50, for example at a temperature of about 43° C. and a pressure of about 24 bar. Also, the first fluid 4 flowing through the supply pipe 15 at least between the branch point 21 and the pumping element 19 is the same as the first fluid flowing through the second pipe 16 between the third heat exchange element 38 and the cooling device 50. , ie a temperature of about 43° C. and a pressure of about 24 bar.

Thus, from the above it follows that the pump element 19 defines two portions of the supply tube 15 , a front portion 23 in front of the pump element 19 and a rear portion 25 behind the pump element 19 . More specifically, the front portion 23 of the supply tube 15 extends from the flow dividing point 21 to the pump element 19 , while the rear portion 25 of the supply tube 15 extends from the pump element 19 to the consumer 17 .

According to the invention, the pump element 19 raises the pressure of the first fluid 4 flowing through the supply pipe 15 by at least 5 bar. Advantageously, the pump element 19 raises the pressure of the first fluid 4 flowing through the supply pipe 15 by approximately 10-20 bar, not exceeding 35 bar. For example, the pressure of the first fluid 4 flowing through the front portion 23 is approximately 24 bar, while the pressure of the first fluid 4 flowing through the rear portion 25 is approximately 45 bar. Advantageously, the pressure of the first fluid 4 flowing through the rear portion 25 is approximately 35-55 bar. Therefore, the pressure delivered to the consumer 17 in this case is a combination of the force produced by the compression element(s) 14 and the force produced by the pump element 19, resulting in a smaller, cheaper and more It should be noted that a reliable pumping element can be used to liquefy the first fluid, manage the pressure of the second fluid and supply fuel to the consuming unit.

Furthermore, the temperature of the first fluid 4 flowing through the supply pipe 15 is, for example, 20°C to 40°C. At this temperature, in particular when the pressure of the first fluid 4 is between 35 and 55 bar, the first fluid 4 is liquid.

According to an alternative of the invention, the pump element 19 is arranged directly at the fluid outlet of the phase separator 44 opening into the second pipe 16 . In this arrangement the pump element 19 delivers the first fluid 4 through the second line 16 directly to the first tank 2 and through the supply line 15 to the consuming machine 17 .

Furthermore, circuit 1 includes a control valve 27 for controlling the flow rate of first fluid 4 through supply tube 15 . The control valve 27 allows the first fluid 4 to pass through so that the control valve 27 can regulate the amount of the first fluid 4 flowing to the consumer 17 . For example, the control valve 27 adjusts the flow rate of the first fluid 4 through the supply pipe 15 so that the flow rate of the first fluid 4 meets the requirements of the consumption unit. The control valve 27 thus adapts the flow rate of the first fluid 4 through the supply line 15 to the demand of the consumer 17 for fuel.

Advantageously, the control valve 27 is attached to the forward portion 23 of the supply pipe 15 . That is, the control valve 27 is arranged on the supply pipe 15 between the flow dividing point 21 and the pump element 19 . The control valve 27 thus regulates the flow rate of the first fluid 4 through the supply pipe 15 upstream of the pump element 19 . However, a circuit in which the control valve 27 is mounted between the pump element 19 and the consumer 17, ie in the rear portion 25 of the supply tube 15, would not depart from the scope of the invention.

According to another embodiment shown in FIG. 3, circuit 1 includes a conveying pipe 31 extending between management pipe 20 and supply pipe 15 . Thus, the carrier pipe 31 fluidly connects the management pipe 20 to the supply pipe 15 .

Towards this end, the management pipe 20 includes an intersection section 33 of the conveying pipe 31 and the management pipe 20 , so that at least a portion of the second fluid 8 flowing through the management pipe 20 passes through the conveying pipe 31 at the intersection section 33 . through to supply pipe 15 . The crossover section 33 is in this case located on the first portion 80 of the management pipe 20, but could be located on the second portion 82 of the management pipe 20 without thereby departing from the scope of the invention. do not have.

On the one hand, the supply tube 15 comprises a branch section 35 with the carrier tube 31 , so that the second fluid 8 flowing through the carrier tube 31 flows through the branch section 35 through the supply tube 15 . In this arrangement, the consumer 17 can be supplied with the second fluid 8 and the consumer 17 can use the second fluid 8 as fuel. The branch section 35 is in this case arranged in the front part 23 of the supply pipe 15, but it can also be arranged in the rear part 25 of the supply pipe 15 without departing from the scope of the invention.

Furthermore, in the branch section 35 , the second fluid 8 from the management pipe 20 flowing through the carrier pipe 31 is mixed with the first fluid 4 flowing through the supply pipe 15 . Note that downstream of the branch section 35 a mixture of the first fluid 4 and the second fluid 8 flows to the consumer machine 17 .

Further, the carrier pipe 31 includes a regulating valve 37 for adjusting the flow rate of the second fluid 8 flowing through the carrier pipe 31 . Note that the regulating valve 37 allows the second fluid 8 to flow through the carrier pipe 31 to the supply pipe 15 and to the consumer machine 17 . Note that the flow rate of the second fluid 8 in the carrier tube 31 is controlled by a regulating valve 37 so that the amount of the second fluid 8 flowing through the supply tube 15 is regulated by this regulating valve 37 .

Note that the consuming machine 17 can use the first fluid 4 as fuel, but also the second fluid 8 and/or a mixture of the first fluid 4 and the second fluid 8 as fuel.

A second embodiment of the invention will now be described with particular reference to FIG. The elements that differentiate the second embodiment from the first embodiment are described below. Refer to the detailed description of the first embodiment for identical elements.

As shown in FIG. 2, the circuit 1 includes a first pipe 92 and a second pipe 94 each independently extending between the second pipe 16 and the first pipe 12 .

The first pipe 92 is connected on the one hand to the second pipe 16 and on the other hand to the third section 32 of the first pipe 12 between the second heat exchange element 42 and the third compression element 14c. The first fluid 4 flowing through the first pipe 92 mixes with the first fluid 4 flowing through the third portion 32 of the first pipe 12 at a location between the second heat exchange element 42 and the third compression element 14c. Please note.

The circuit 1 includes a first cooling device 96 attached to the second pipe 16 and the first pipe 92 , the first cooling device 96 being connected to a first heat exchanger 98 and a first heat exchanger upstream of the first heat exchanger 98 . and a first expansion device 100 disposed on the pipe 92 . The first heat exchanger 98 is configured to exchange thermal energy between the first fluid 4 flowing through the first pipe 92 and the first fluid 4 flowing through the second pipe 16 . To this end, the first heat exchanger 98 includes a first conduit 102 forming the second pipe 16 and a second conduit 104 forming the first pipe 92 . The first fluid 4 flowing through the second pipe 16 passes through the first conduit 102 through the first heat exchanger 98 and the first fluid 4 flowing through the first pipe 92 passes through the second conduit 104 to the first heat exchanger 98 . Note that it passes through vessel 98 .

Furthermore, it should be noted that the first intersection 521 of the first pipe 92 and the second pipe 16 is located between the phase separator 44 and the first cooling device 96 . Thus, the first fluid 4 flowing through the first intersection 521 can continue to flow through the second pipe 16 to the first cooling device 96 and/or continue to flow through the first pipe 92 to the first pipe 12 .

The first expansion device 100 in this case causes the pressure of the first fluid 4 in a liquid state flowing through the first pipe 92 to be approximately the same as the pressure of the first fluid 4 in a gaseous state flowing through the third portion 32 of the first pipe 12 . configured to lower to For example, the pressure of the first fluid 4 flowing downstream of the first cooling device 96 is approximately 10.5 bar and the first expansion device 100 reduces the pressure of the first fluid 4 flowing through the first pipe 92 to from a pressure of about 24 bar upstream of the first expansion device 100 to a pressure of about 10.5 bar downstream of the first expansion device 100 .

Heat exchange between the first fluid 4 flowing through the second pipe 16 and the first fluid 4 flowing through the first pipe 92 is specifically in the first heat exchanger 98, more specifically in the first conduit 102 and the first pipe 92. 2 conduit 104 . The first fluid 4 flowing through the first conduit 102 transfers thermal energy to the expanded first fluid 4 flowing through the second conduit 104 . In other words, the first fluid 4 flowing through the second conduit 104 cools the first fluid 4 flowing through the first conduit 102 and the temperature of the first fluid 4 flowing through the first conduit 102 decreases while the second conduit 104 cools. The temperature of the first fluid 4 flowing through increases. The increase in temperature of the first fluid 4 flowing through the second conduit 104 causes said first fluid 4 to transition from a two-phase state to a gaseous state.

As shown in FIG. 2, the second pipe 94 is connected to the second pipe 16 on the one hand and the second section 30 of the first pipe 12 between the first heat exchange element 40 and the second compression element 14b on the other hand. connected to The first fluid 4 flowing through the second pipe 94 mixes with the first fluid 4 flowing through the second portion 30 of the first pipe 12 at a location between the first heat exchange element 40 and the second compression element 14b. Please note.

Furthermore, the second pipe 94 is connected to the second pipe 16 downstream of the first cooling device 96 . Note that the second intersection 522 of the second pipe 94 and the second pipe 16 is located between the first cooling device 96 and the phase separation device 62 . The first fluid 4 flowing through the second pipe 94 originates from the first fluid 4 cooled by the first cooling device 96 and flowing through the second pipe 16 .

Circuit 1 includes a second cooling device 106 attached to a second pipe 16 and a second pipe 94 , the second cooling device 106 includes a second heat exchanger 108 and a second pipe upstream of the second heat exchanger 108 . and a second inflation device 110 disposed on 94 . The second heat exchanger 108 is configured to exchange thermal energy between the first fluid 4 flowing through the second pipe 94 and the first fluid 4 flowing through the second pipe 16 downstream of the first cooling device 96 . . Towards this end, the second heat exchanger 108 includes a first conduit 112 forming the second pipe 16 and a second conduit 114 forming the second pipe 94 . The first fluid 4 flowing through the second pipe 16 passes through the second heat exchanger 108 through the first conduit 112 and the first fluid 4 flowing through the second pipe 94 passes through the second conduit 114 to the second heat exchanger 108 . Note that it passes through vessel 108 .

The second expansion device 110 in this case causes the pressure of the first fluid 4 in a liquid state flowing through the second pipe 94 to be approximately the same as the pressure of the first fluid 4 in a gaseous state flowing through the second portion 30 of the first pipe 12 . configured to lower to For example, the pressure of the first fluid 4 flowing downstream of the second cooling device 106 is about 3 bar and the second expansion device 110 reduces the pressure of the first fluid 4 flowing through the second pipe 94 to from a pressure of about 24 bar at , to a pressure of about 3 bar downstream of the second expansion device 110 .

The expansion of the first fluid 4 flowing through the second pipe 94 from a pressure of approximately 24 bar to a pressure of approximately 3 bar reduces the temperature of the first fluid 4 flowing through the second conduit 114 . The first fluid 4 flowing between the second expansion device 110 and the second conduit 114 is in a two-phase state and the first fluid 4 evaporates as it passes through the second conduit 114 .

Heat exchange between the first fluid 4 flowing through the second pipe 16 and the first fluid 4 flowing through the second pipe 94 occurs specifically in the second heat exchanger 108, more specifically in the first conduit 112 and the second pipe 94. 2 conduit 114 . The first fluid 4 flowing through the first conduit 112 transfers thermal energy to the expanded first fluid 4 flowing through the second conduit 114 . In other words, the first fluid 4 flowing through the second conduit 114 cools the first fluid 4 flowing through the first conduit 112 and the temperature of the first fluid 4 flowing through the first conduit 112 decreases while the second conduit 114 cools. The temperature of the first fluid 4 flowing through increases. The increase in temperature of the first fluid 4 flowing through the second conduit 114 causes said first fluid 4 to transition from a two-phase state to a gaseous state.

A branch 116 of the cooling pipe 18 and the second pipe 16 is arranged between the first cooling device 96 and the second cooling device 106 . The first fluid 4 flowing in the second pipe 16 downstream of the first cooling device 96 flows through the cooling pipe 18 to the cooling unit 24 or through the second pipe 94 to the first pipe 12 or the second pipe 16 Note that it can flow to the first tank 2 through the . Advantageously, the branch 116 of the cooling pipe 18 and the second pipe 16 is attached between the second intersection 522 of the second pipe 16 and the second pipe 94 and the first cooling device 96 .

In this configuration, the cooling pipe 18 extends between the second pipe 16 and the second pipe 94 and the cooling pipe 18 is connected to the second pipe 94 downstream of the second cooling device 106 . Here, the first gaseous fluid 4 flowing through the cooling pipe 18 downstream of the cooling unit 24 is subjected to a second cooling before being incorporated into the first gaseous fluid 4 flowing through the second portion 30 of the first pipe 12 . Note that it mixes with the gaseous first fluid 4 flowing through the second pipe 94 downstream of the device 106 .

Therefore, from the above it follows that part of the first fluid 4 is recycled by the management system 1 and this part of the first fluid 4 mainly cools the first fluid 4 and/or the second fluid 8. will help you to

According to one feature of the invention, the supply pipe 15 extends from the cooling pipe 18 to the consumer 17 and the branch 116 of the supply pipe 15 and the cooling pipe 18 is arranged between the cooling device 96 and the cooling unit 24 . It should be noted that the first fluid 4 flowing through the supply pipe 15 is first cooled while passing through the first cooling device 96 before flowing through the supply pipe 15 to the consumer 17 .

Furthermore, the supply pipe 15 extends from the cooling pipe 18 to the consumer 17 , and the branching point 29 of the supply pipe 15 and the cooling pipe 18 is arranged upstream of the expansion element 86 of the cooling unit 24 . It should be noted that the first fluid 4 flowing through the cooling pipe 18 to the expansion element 86 of the cooling unit 24 can flow through the supply pipe 15 to the consumer 17 at the junction 29 .

In this embodiment, the first fluid 4 flowing through the supply pipe 15 to the consumer 17 is cooled by the first cooling device 96 compared to the first embodiment. An advantage of this embodiment is that the first fluid 4 is more preferably liquid when flowing through the supply pipe 15 to the consumer 17, optimizing the use of the first fluid 4 as fuel by the consumer 17. It is in. Furthermore, by reducing the temperature of the first fluid 4, the risk of cavitation occurring in the pump element 19 is reduced.

However, the invention is not limited to the means and arrangements described and shown herein, but also to all equivalent means and arrangements and to any technically working combination of such means. reach. Specifically, all of the elements that change the pressure, temperature, and/or state of the first fluid 4 and/or the pressure, temperature, and/or state of the second fluid 8 are those elements herein Modifications are possible without detrimental to the invention, provided that they provide the functionality described in .

Claims (12)

A circuit (1) through which a first fluid (4) contained in a first tank (2) and a second fluid (8) contained in a second tank (6) can flow, said first fluid (4) has a boiling point lower than the boiling point of said second fluid (8) and said circuit (1) comprises a first pipe ( 12), wherein said first fluid (4) taken from said first tank (2) in gaseous state is intended to flow through said first pipe (12), said heat exchange element (38) , 40, 42) are adapted to condense said first fluid (4) and said circuit (1) is a second pipe extending from said heat exchange element (38, 40, 42) to said first tank (2). (16), said first fluid (4) in liquid state and/or two-phase state is intended to flow through said second pipe (16), said circuit (1) being connected to said second tank ( 6) for managing the condition of said second fluid (8), through which said second fluid (8) taken in liquid state from , said circuit (1) comprises a supply pipe (15) extending from said second pipe (16) to said consumer (17) for supplying at least said first fluid (4) to a consumer (17) using said first fluid (4) as fuel. ), wherein said supply tube (15) is configured to flow through at least said first fluid (4) in liquid state, said supply tube (15) at least said first fluid in said supply tube (15) A circuit (1), characterized in that it comprises at least one pumping element (19) for increasing the pressure of (4). said first pipe (12) comprising at least one cooling pipe (18) intended for the flow of said first fluid (4), extending from said second pipe (16) to said first pipe (12); includes at least a first compression element (14, 14a) and a second compression element (14, 14b, 14c), said cooling pipe (18) connecting said first compression element (14, 14a) and said second compression element A circuit (1) according to claim 1, connected to said first pipe (12) between (14, 14b, 14c). At least one cooling unit (24) for cooling the second fluid (8) in a liquid state flowing through the management pipe (20) for managing the state of the second fluid (8), the cooling unit ( 24) passes through said at least one cooling pipe (18) extending from said second pipe (16) to said first pipe (12) and through which said first fluid (4) is intended to flow. 3. Circuit (1) according to claim 1 or 2, caused by evaporation of the flowing first fluid (4). Said cooling unit (24) comprises at least a heat exchanger (84) and an expansion element (86), said heat exchanger (84) connecting said first fluid (4) flowing through said cooling pipe (18) and said management fluid (4). 4. Circuit (1) according to claim 3, for exchanging thermal energy between said second fluid (8) flowing in a pipe (20). The heat exchanger (84) includes at least a first passage (88) forming the cooling pipe (18) and a second passage (90) forming the management pipe (20), and the expansion element ( 5. Circuit (1) according to claim 4, wherein 86) is arranged between said first passage (88) and said second pipe (16). Said circuit (1) comprises at least one pipe (48) extending from said second pipe (16) to said first pipe (12) through which said first fluid (4) flows, wherein said circuit (1) comprises said second pipe ( at least one cooling device (50) for cooling said first fluid (4) flowing through said pipe (48), wherein the cold air generated by said cooling device (50) cools said first fluid (4) flowing through said pipe (48); 6. The circuit (1) according to any one of claims 1 to 5, resulting from the evaporation of ). Said supply pipe (15) is connected to said second pipe at a branch point (21) arranged on said second pipe (16) between said heat exchange element (38, 40, 42) and said cooling device (50). 7. Circuit (1) according to claim 6, connected to a pipe (16). Said supply pipe (15) enters said second pipe (16) at said diversion point (21) arranged on said second pipe (16) between a separation element (44) and said cooling device (50). Circuit (1) according to claim 7, connected. at least one said phase separation element (44) for said first fluid (4) disposed on said second pipe (16), said first fluid (4) said phase separation element (44) through said second pipe to said first tank (2), said circuit (1) comprising a gas pipe (46) extending from said separating element (44) to said second pipe (16). A circuit (1) according to any one of Clauses 1-8. Said supply pipe (15) extends from said cooling pipe (18) to said consumer device (17) and a junction (29) between said supply pipe (15) and said cooling pipe (18) is connected to said cooling device A circuit (1) according to any one of claims 3 to 5 as dependent on claim 6, arranged between (50) and said cooling unit (24). Said supply pipe (15) extends from said cooling pipe (18) to said consumer (17) and said junction (29) between said supply pipe (15) and said cooling pipe (18) is connected to said cooling 11. A circuit (1) as claimed in claim 10 when dependent on claim 4, arranged between the expansion element (86) of the unit (24) and the cooling device (50). A circuit (1) according to any preceding claim, comprising a control valve (27) for controlling the flow rate of said first fluid (4) through said supply pipe (15).

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