JP2022186666A - Management system for managing state of fluid - Google Patents

Abstract

To reduce overall consumed energy when different types of liquefied gases are stored in a first tank and a second tank.SOLUTION: A management system 1 manages the state of a first fluid 4 stored in a first tank 2, and the state of a second fluid 8 whose boiling point is higher than that of the first fluid 4 stored in the second tank 6. The management system 1 includes a first pipe 12 through which the first fluid 4 taken from the first tank 2 in a gaseous state flows, includes a second pipe 16 through which the first fluid 4 in a liquid state and/or in a two-phase state flows, includes a cooling pipe 18 extending from the second pipe 16 to the first pipe 12, through which the first fluid 4 is intended to flow, and includes a management pipe 20 through which the second fluid 8 flows. The management system 1 includes at least one cooling unit 24 for cooling the second fluid 8 flowing through the management pipe 20. The cool air formed by the cooling unit 24 is generated by evaporation of the first fluid 4 flowing through the cooling pipe 18.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. . Thus, for example, such a management system is arranged to liquefy a first fluid on the one hand and a second fluid independently of the re-liquefaction of the first fluid on the other hand.

However, each of the management systems generally includes multiple compression elements for compressing the vaporized first fluid and/or the vaporized second fluid, which multiple compression elements can increase the pressure of said gas. These compression elements are generally large and the management system takes up a significant amount of surface area and/or volume on the vessel.

Furthermore, for redundancy reasons, it is customary to add additional thermal conditioning circuits, which further increase the surface area and/or volume occupied by the management system on board the vessel. Adding this additional thermal conditioning circuit also introduces additional costs on top of those already required to install and use the rest of the management system.

The present invention aims at reducing the space occupied by such compression elements in order to reduce the volume occupied by such management systems and the energy consumed by such management systems. The invention proposes a system for managing the state of the vaporized first fluid, which also allows cooling of the second fluid in liquid state, so that it can be used to manage the state of the second fluid. The technical resources required and the financial impact of installing such a condition management system can be reduced.

The present invention mainly relates to a management system for managing the state of a first fluid contained in a first tank and the state of a second fluid contained in a second tank, the first fluid being the same pressure as the second fluid. having a boiling point lower than that of the two fluids, the management system comprising a first conduit intended for the flow of a first fluid taken from the first tank in a gaseous state and configured to open into the first tank; a first pipe extending from a gas inlet to a heat exchange element configured to condense a first fluid, the first pipe including at least a first compression element and a second compression element; and/or second piping intended for flow of a first fluid in a two-phase state, the second piping extending from the heat exchange element to a second port configured to open into the first tank. , the management system includes at least one cooling pipe extending from the second pipe to the first pipe and intended for the flow of the first fluid and connected to the first pipe between the first compression element and the second compression element; and the management system includes at least one management conduit through which the second fluid is intended to flow for managing the condition of the second fluid, the management system cooling the second fluid flowing through the management conduit. at least one cooling unit for cooling, wherein the cold air generated by the cooling unit is caused by evaporation (boil-off) of the first fluid flowing through the cooling pipes.

According to one optional configuration, the management system includes a first fluid and a second fluid, specifically these fluids flow through the management system.

A management system controls the condition of the first and second fluids contained in the first and second tanks respectively, ie at least the pressure and/or the temperature of the first or second fluids. 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. Furthermore, the vaporized second fluid flowing through the second tank is also cooled and contacted with the cooled second fluid flowing through the control piping downstream of the cooling unit and/or the second fluid sprayed into the tank. can condense on contact with

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, ie the pressure of a portion of this first fluid is reduced, so that the first fluid lowers the temperature of the second fluid.

The first and second fluids are, for example, petroleum gas, the first fluid is, for example, a mixture of 92% propane and 8% butane, having a boiling point of −47° C. at atmospheric pressure, and the second fluid is, for example, It consists of 100% butane and has a boiling point of 0°C at atmospheric pressure.

According to another embodiment of the invention, the first fluid is a natural gas such as methane and has a boiling point of about −160° C., ie the first fluid is at atmospheric pressure and at a temperature below −160° C. In some cases it is liquid.

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 8 is 100% ammonia with an evaporation temperature of -33°C. consists of

The above temperatures are measured at atmospheric pressure.

Furthermore, the condensation of the first fluid within the first pipe occurs due to the exchange of thermal energy between the first fluid and the coolant within the heat exchange element.

According to an optional feature of the invention, the cooling unit includes at least a heat exchanger and an expansion element attached to a cooling pipe between the second pipe and the heat exchanger, the heat exchanger connecting the cooling pipe to the cooling pipe. It is configured to exchange heat between the flowing first fluid and the second fluid flowing through the management piping.

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.

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 an 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, wherein an expansion element is located between the second pipe and the first passageway. placed in between.

Note that in this configuration, the pressure of the first fluid flowing through the cooling pipe is lowered by the expansion element before the first fluid flows through the first passageway of the heat exchanger.

According to an optional feature of the invention, the management system includes at least one pump element arranged on the management piping upstream of the cooling unit. A pumping element is configured to circulate the second fluid through the control line.

According to an optional feature of the invention, the management system includes at least one pipe extending between the second pipe and the first pipe, the pipe extending from the first pipe between the first compression element and the second compression element. and the management system includes at least one cooling device for cooling the first fluid flowing through the second pipe, the cold generated by the cooling device resulting from evaporation of the first fluid flowing through the pipe.

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 an optional feature of the invention, the cooling device comprises at least a heat exchanger and an expansion device, the heat exchanger comprising a first passage forming a second pipe and a second passage forming a pipe, wherein the expansion The device is disposed on the pipe between the second pipe and the second passageway, and the heat exchanger is configured to exchange heat between the first fluid flowing through the second pipe and the first fluid flowing through the pipe.

More specifically, the first fluid flowing through the pipe is expanded by an expansion device before flowing through the heat exchanger. As the first fluid flowing through the second pipe passes through the heat exchanger, it transfers thermal energy to the expanded first fluid flowing through the pipe as it passes through the heat exchanger.

In other words, the first fluid flowing through the pipe and passing through the heat exchanger is warmed and vaporized within the heat exchanger by gaining thermal energy from the first fluid flowing through the second pipe. 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 first fluid flowing through the second pipe is lowered. Specifically, thermal energy is transferred from the first fluid flowing through the second pipe to the first fluid flowing through the pipe. approaches the temperature of the first fluid flowing through the pipe.

According to an optional feature of the invention, the management system comprises a first heat exchange element for heat exchange between the first fluid and the coolant and a first heat exchange element for heat exchange between the first fluid and the coolant. at least two heat exchange elements, the first heat exchange element mounted between the first compression element and the second compression element, and a pipe connected to the first pipe between the first heat exchange element and the second compression element. be. The first fluid in gaseous state flowing through the pipe is mixed with the first fluid in gaseous state flowing through the first pipe at a location between the first heat exchange element and the second compression element.

According to an optional feature of the invention, a cooling pipe is connected to the pipe between the first pipe and the cooling device. Note that the gaseous first fluid flowing through the cooling pipe mixes with the gaseous first fluid flowing through the pipe after passing through the cooling device.

According to an optional feature of the invention, the management system includes a branch of a cooling pipe and a second pipe mounted between a second port located in the first tank and the cooling device.

According to an optional feature of the invention, the management system comprises a first cooling device for cooling the first fluid flowing through the second pipe and a second cooling device for cooling the first fluid flowing through the second pipe. and the management system includes a branch of the second pipe and the cooling pipe mounted downstream of the second cooling device.

According to an optional feature of the invention, the management system includes a branch of the cooling pipe and the second pipe mounted between the second compression element and the cooling device.

According to an optional feature of the invention, the management system comprises a first cooling device for cooling the first fluid flowing through the second pipe and a second cooling device for cooling the first fluid flowing through the second pipe. and the management system includes a branch of the cooling pipe and the second pipe mounted upstream of the first cooling device.

According to an optional feature of the invention, the management system includes at least one phase separator for the first fluid attached to the second pipe between the intersection of the pipe and the second pipe and the second compression element. and the management system includes a gas pipe extending between the phase separator and the second pipe, the gas pipe being connected to the second pipe between the intersection of the pipe and the second pipe and the cooling device, wherein the liquid state is the first fluid can flow from the phase separator through the second pipe to the intersection of the pipe and the second pipe, and the first fluid in gaseous state can flow from the phase separator through the gas pipe to the second pipe; can flow.

According to an optional feature of the invention, the management system includes a phase separator for the first fluid mounted in the second pipe downstream of the cooling device, the management system between the phase separator and the first pipe. and a return line through which the first fluid in gaseous state flows.

According to an optional feature of the invention, the management system includes a first pipe extending between the first pipe and the second pipe and a second pipe extending between the first pipe and the second pipe, the management system comprising: a third compression element attached to the first pipe, the second compression element attached between the first compression element and the third compression element, and the first pipe between the second compression element and the third compression element. A first cooling device opening into the first pipe, the second pipe opening into the first pipe between the first compression element and the second compression element, and the management system for cooling the first fluid flowing through the second pipe. and a second cooling device for cooling the first fluid flowing through the second pipe, wherein the cold generated by the first cooling device is generated by evaporation of the first fluid flowing through the first pipe, and the second cooling device The cold air produced is caused by evaporation of the first fluid flowing through the second pipe, and the first cooling device is attached to the second pipe upstream of the second cooling device. In this case, it should be noted that the first fluid flowing through the second pipe to the first tank is cooled first in the first cooling device and second time in the second cooling device.

According to an optional feature of the invention, the cooling pipe is connected to the second pipe between the first cooling device and the second cooling device.

According to an optional feature of the invention, the cooling pipe is connected to a second pipe downstream of the second cooling device.

According to an alternative, the cooling pipe is connected to the second pipe upstream of the first cooling device.

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 first embodiment of a management system according to the invention; Figure 2 schematically represents a second embodiment of a management system according to the invention; Figure 3 schematically represents a third embodiment of a management system according to the invention; Figure 4 schematically represents a fourth embodiment of a management system according to the invention; 5 schematically represents a fifth embodiment of a management system according to the invention;

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.

Further, the terms "upstream" and "downstream" as used in the description below refer to the first fluid and/or the second fluid within a management system according to any of the embodiments described in detail below. Point in the direction of circulation.

FIG. 1 shows a management system 1 for managing the state of 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. indicates The first tank 2 , the second tank 6 and/or the management system 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, for example, petroleum gas such as 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.

According to an alternative of the invention, the second tank 6 contains only a primary layer and the primary insulation barrier is in direct contact with the environment outside the second tank 6 . Note that in this alternative the second tank 6 has no secondary layer and insulation is provided only by the primary insulation barrier of the primary layer.

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 management system 1 is arranged to re-liquefy at least part of the gaseous first fluid 4 present in the uppermost part 10 of the first tank 2 on the one hand and to a consuming machine using the first fluid 4 as fuel on the other hand. It is arranged to supply a first fluid 4 . Towards this end, the management system 1 includes on the one hand a first pipework 12 through which the first fluid 4 flows from the first tank 2 to the plurality of compression elements 14 and the first fluid 4 in a liquid state and/or a second pipe 16 flowing therein in two-phase condition from the first pipe 12 to the first tank 2, and on the other hand a pipeline 45 extending between the second pipe 16 and the consuming machine. Furthermore, the management system 1 includes a cooling pipe 18 through which the first fluid 4 flows from the second pipe 16 to the first pipe 12 .

The management system 1 further comprises at least one management line 20 for managing the condition of the second fluid, through which at least a portion of the second fluid 8 flows from the second tank 6 to the second tank 6 . flow to the liquid outlet 22 for the second fluid 8 of . 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, liquid outlet 22 is in the form of a spray bar that facilitates distribution of second fluid 8 sprayed onto top 11 .

According to the invention, the management system 1 comprises a cooling unit 24 for cooling the liquid state second fluid 8 flowing in the management pipe 20 , the cold air generated by the cooling unit 24 cooling the first fluid 4 flowing in the cooling pipe 18 . It is the result of evaporation. 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 .

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 consuming machine.

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 containing glycol, 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.

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 then flows to the second pipe 16 and/or through the pipeline 45 to the consuming machine. The management system 1 comprises a gas pipe 46 through which the first fluid 4 flows in gaseous form from the phase separator 44 to the second pipe 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.

The phase separator 62 includes a phase separator main section 66 and an expansion element 68 positioned on the second pipe 16 upstream of the 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 is supplied to the first tank 2 in order to match the pressure of the first fluid 4 with the pressure of the first fluid 4 contained in the first tank 2 . Note that before reaching the first tank 2 it expands, 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.

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, cooling tube 18 is connected to pipe 48 downstream of 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 device 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.

According to the first embodiment shown in FIG. 1 , the first gaseous fluid 4 flowing through the cooling pipe 18 downstream of the heat exchanger 84 is the first gaseous fluid flowing through the pipe 48 downstream of the cooling device 50 . 4, this mixture is then entrained in the gaseous first fluid 4 flowing through the second portion 30 of the first pipe 12 between the first heat exchange element 40 and the second compression element 14b.

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

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.

In the second embodiment, the pipe 48 is connected to the first pipe 12 at the third portion 32, ie between the second heat exchange element 42 and the third compression element 14c. Note that the gaseous first fluid 4 flows through the pipe 48 downstream of the cooling device 50 to the third portion 32 of the first pipe 12 . The first fluid 4 in gaseous state flowing through the pipe 48 downstream of the cooling device 50 is in gaseous state 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. is mixed with the first fluid 4 of

The expansion device 56, in this case, converts the pressure of the first fluid 4 flowing through the pipe 48 into a first gaseous state flowing through the third section 32 of the first pipe 12 between the second heat exchange element 42 and the third compression element 14c. It is arranged to reduce the pressure to approximately the same as the pressure of the fluid 4 . For example, the pressure of the first fluid 4 flowing downstream of the cooling device 50 is about 10.5 bar and the expansion device 56 reduces the pressure of the first fluid 4 flowing through the pipe 48 to about 24 bar upstream of the expansion device 56. The pressure is changed to about 10.5 bar downstream of the expansion device 56 .

As shown in FIG. 2, cooling pipe 18 extends between second pipe 16 and second portion 30 of first pipe 12 . The cooling pipe 18 is directly connected to the first pipe 12 at the second portion 30 . The gaseous first fluid 4 flowing through the cooling pipe 18 downstream of the cooling unit 24 is gaseous 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. mixed with the first fluid 4 in the state.

The expansion element 86 is in this case configured to reduce the pressure of the first fluid 4 flowing through the cooling tube 18 to approximately the same pressure as the pressure of the gaseous first fluid 4 flowing through the second portion 30 of the first piping 12 . . For example, the pressure of the first fluid 4 flowing through the cooling tube 18 downstream of the cooling unit 24 is approximately 3 bar, and the expansion element 86 reduces the pressure of the first fluid 4 flowing through the cooling tube 18 to approximately A pressure of 24 bar is changed to a pressure of about 3 bar downstream of the expansion element 86 .

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

As shown in FIG. 3, the management system 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 management system 1 includes a first cooling device 96 attached to the second pipe 16 and the first pipe 92 , the first cooling device 96 comprising 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. 3, 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 .

The management system 1 includes a second cooling device 106 attached to the second pipe 16 and the second pipe 94 , the second cooling device 106 including a second heat exchanger 108 and a second heat exchanger 108 upstream of the second heat exchanger 108 . and a second expansion device 110 disposed on the pipe 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 approximately 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.

According to the invention, the 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 a fourth embodiment of the invention shown in FIG. 4, the cooling pipe 18 and the branch 116 of the second pipe 16 are mounted between the second cooling device 106 and the phase separator 62 . It is noted here that the liquid state first fluid 4 flowing downstream of the second cooling device 106 flows through the second line 16 to the phase separator 62 or through the cooling line 18 to the cooling unit 24 . sea bream.

Thus, from the above, this configuration allows the first fluid 4 to reach the expansion element 86 at a lower temperature than the configurations previously described in the first, second and third embodiments. becomes. After passing through expansion element 86 , first fluid 4 is expanded to further reduce its temperature, thereby optimizing the cooling of second fluid 8 occurring in heat exchanger 84 . In other words, in the example shown here, the first fluid 4 flowing between the expansion element 86 and the heat exchanger 84 is It has a much lower temperature than the flowing first fluid 4, which allows the temperature of the second fluid 8 in the heat exchanger 84 to be reduced more efficiently.

According to a fifth embodiment of the invention shown in FIG. 5, the cooling pipe 18 and the branch 116 of the second pipe 16 are mounted between the phase separator 44 and the first cooling device 96 . Here, the first fluid 4 in a liquid state flowing downstream of the phase separator 44 passes through the second pipe 16 or the first pipe 92 to the first cooling device 96, or through the cooling pipe 18 to the cooling unit 24. Note that it flows. More specifically, the branch 116 of the second pipe 16 and the cooling pipe 18 is attached to the first intersection 521 of the second pipe 16 and the first pipe 92 . However, the branch 116 of the second pipe 16 and the cooling pipe 18 is located between the intersection 521 of the second pipe 16 and the first pipe 92 and the phase separator 44, or the intersection of the second pipe 16 and the first pipe 92. A management system 1 mounted between 521 and the first cooling device 96 would not depart from the scope of the invention.

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 (15)

A management system (1) for managing the condition of a first fluid (4) contained in a first tank (2) and the condition of a second fluid (8) contained in a second tank (6), , said first fluid (4) has a boiling point lower than that of said second fluid (8) at the same pressure, and said management system (1) controls said liquid taken from said first tank (2) in gaseous state. A first conduit (12) through which a first fluid (4) is intended to flow from a gas inlet (26) configured to open into said first tank (2) to said first fluid (4). ), said first piping (12) extending to a heat exchange element (38, 40, 42) configured to condense a first compression element (14a) and a second compression element (14a). said management system (1) comprising at least an element (14b) and a second pipe (16) intended for the flow of said first fluid (4) in liquid and/or two-phase state, said comprising a second pipe (16) extending from a heat exchange element (38, 40, 42) to a second port (65) configured to open into said first tank (2), said management system (1) comprising at least one cooling pipe (18) extending from said second pipe (16) to said first pipe (12) and intended for said first fluid (4) to flow through said first compression element (14a); and a cooling pipe (18) connected to said first pipe (12) between said second compression element (14b) and said management system (1) is intended to allow said second fluid (8) to flow at least one management line (20) for managing the condition of said second fluid (8), wherein said management system (1) controls said second fluid (8) flowing through said management line (20). wherein cold air is produced by said cooling unit (24) and is caused by evaporation of said first fluid (4) flowing through said cooling pipes (18) , a management system (1). The cooling unit (24) comprises a heat exchanger (84) and an expansion element (86) attached to the cooling pipe (18) between the second pipe (16) and the heat exchanger (84). wherein said heat exchanger (84) exchanges heat between said first fluid (4) flowing through said cooling pipe (18) and said second fluid (8) flowing through said management pipe (20) 2. Management system (1) according to claim 1, adapted to. 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 ( 3. Management system (1) according to claim 2, wherein 86) is arranged between said second pipe (16) and said first passageway (88). A management system (1) according to any one of the preceding claims, comprising at least one pump element (78) arranged on said management piping (20) upstream of said cooling unit (24). At least one pipe (48) extending between said second pipe (16) and said first pipe (12), wherein said pipe (48) comprises said first compression element (14a) and said second compression element ( 14b) connected to said first pipe (12), said management system (1) comprises at least one cooling device (50) for cooling said first fluid (4) flowing through said second pipe (16). ), wherein the cold produced by the cooling device (50) results from evaporation of the first fluid (4) flowing through the pipe (48). (1). The cooling device (50) includes at least a heat exchanger (54) and an expansion device (56), and the heat exchanger (54) comprises a first passage (58) forming the second pipe (16) and the pipe. (48), said expansion device (56) being disposed on said pipe (48) between said second pipe (16) and said second passageway (60). , said heat exchanger (54) is configured to exchange heat between said first fluid (4) flowing through said second pipe (16) and said first fluid (4) flowing through said pipe (48); 6. Management system (1) according to claim 5, wherein the management system (1) a first heat exchange element (38, 40, 42) for heat exchange between said first fluid (4) and cooling liquid; and for heat exchange between said first fluid (4) and said cooling liquid. a second heat exchange element (38, 40, 42), said first heat exchange element (38, 40, 42) being between said first compression element (14a) and said second compression element (14b) and said pipe (48) is connected to said first pipe (12) between said first heat exchange element (40) and said second compression element (14b). management system (1). Management system according to any one of claims 5 to 7, wherein the cooling pipe (18) is connected to the pipe (48) between the first pipe (12) and the cooling device (50). (1). between said second pipe (16) and said cooling pipe (18) mounted between said second port (65) located in said first tank (2) and said cooling device (50); Management system (1) according to any one of claims 5 to 8, comprising a branch (116) of . Claim 5, comprising a branch (116) between said second pipe (16) and said cooling pipe (18) mounted between said second compression element (14b) and said cooling device (50). 9. A management system (1) according to any one of claims 1-8. Said management system (1) is provided in said second pipe (16) between said second compression element (14b) and an intersection (52) between said pipe (48) and said second pipe (16). comprising at least one phase separator (44) for said first fluid (4) installed, said management system (1) being between said phase separator (44) and said second pipe (16); between said cooling device (50) and said intersection (52) between said pipe (48) and said second pipe (16). Connected to the second pipe (16), the first fluid (4) in liquid state passes from the phase separator (44) through the second pipe (16) to the pipe (48) and the second pipe. Able to flow to said intersection (52) between (16), said first fluid (4) in gaseous state passes from said phase separator (44) through said gas pipe (46) to said second A management system (1) according to any one of claims 5 to 10, capable of flowing into a pipe (16). Said management system (1) comprises a separation device (62) for said first fluid (4) mounted in said second pipe (16) downstream of said cooling device (50), said management system ( 1) comprises a return line (64) extending between said separation device (62) and said first line (12) through which said first fluid (4) in gaseous state flows. A management system (1) according to any one of the preceding claims. Said management system (1) comprises a first pipe (92) extending between said first pipe (12) and said second pipe (16), said first pipe (12) and said second pipe (16) a second pipe (94) extending between said management system (1) including a third compression element (14c) attached to said first pipe (12), said second compression element (14b) is arranged beside said first compression element (14a) and said third compression element (14c), said first pipe (92) is between said second compression element (14b) and said third compression element (14c) and said second pipe (94) opens into said first pipe (12) between said first compression element (14a) and said second compression element (14b). and said management system (1) includes a first cooling device (96) for cooling said first fluid (4) flowing through said second pipe (16) and said first fluid flowing through said second pipe (16). and a second cooling device (106) for cooling a fluid (4), wherein cold air generated by said first cooling device (96) flows through said first pipe (92) to said first fluid (4). ) and the cold produced by said second cooling device (106) is caused by evaporation of said first fluid (4) flowing through said second pipe (94), said first cooling device (96) being A management system (1) according to any preceding claim, mounted in said second pipe (16) upstream of said second cooling device (106). 14. Management system (1) according to claim 13, wherein said cooling pipe (18) is connected to said second pipe (16) between said first cooling device (96) and said second cooling device (106). ). Management system (1) according to claim 13 or 14, wherein said cooling pipe (18) is connected to said second pipe (94) downstream of said second cooling device (106).

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