LNG REGASIFICATION DEVICE AND COGENERATOR OF COLD WATER AND COLD DRY AIR

Abstract

A device for regasification of LNG, and cogeneration of fresh water and dry air, having a casing hermetically sealed from the exterior withstanding vacuum conditions, and containing a working fluid in its liquid and gaseous phases; the casing is traversed by t a cryogenic tube through which LNG is fed and regasified natural gas is collected via the other end. The external surface of the cryogenic tube condenses the gaseous working fluid, releasing energy, and evaporative condenser tubes located outside the casing, with the external condensing surface in contact with damp air, and the air vapor contained in the damp air condenses thereupon, generating cold fresh water and releasing energy to the working fluid in its liquid phase which flows through the evaporative condenser and which evaporates, generating a gaseous phase working fluid, which exits through the evaporative condenser and is directed into the casing for the condensation

Claims

1. A device for the regasification of liquefied natural gas, LNG, and the cogeneration of cold fresh water and cold dry air, characterized in that it comprises at least one casing hermetically sealed from the exterior which withstands vacuum conditions and that contains a working fluid in its liquid and gaseous phases, the at least one casing is traversed by at least one cryogenic tube through which liquefied natural gas LNG is fed via one end thereof and regasified natural gas is collected via the other end, the external surface of the at least one cryogenic tube is a condensing surface and the gaseous phase of the working fluid condenses thereupon, releasing energy, and a number of evaporative condenser tubes or chambers located outside the at least one casing with the external condensing surface in contact with damp air and the water vapor contained in the damp air condenses on the external condensing surface of the evaporative condenser tubes or chambers, generating cold fresh water and releasing energy which is absorbed by the working fluid in its liquid phase which flows over the internal evaporative surface of the evaporative condenser tubes or chambers and which evaporates, generating a gaseous phase of the working fluid, which exits through one end of the evaporative condenser tubes or chambers, and is directed into the at least one casing for the condensation thereof.

2. The regasification device according to claim 1, characterized in that it comprises at least one fan, blower or turbine which drives damp air on the external condensing surface of the evaporative condenser tubes or chambers.

3. The regasification device according to claim 1, characterized in that the evaporative condenser tubes or chambers have their internal evaporative surface covered, at least in part, with a capillary structure in the form of microslots, microgrooves, sintered wick or other capillary structure in which the gas-liquid interface of the working fluid curves and flows orderly within the capillary structure without forming liquid films and has its external condensing surface covered, at least in part, with a capillary structure in the form of microslots, microgrooves, sintered wick, or other capillary structure in which the gas-liquid interface of the condensed water curves and flows orderly within the capillary structure without forming water films.

4. The regasification device according to claim 1, characterized in that the external condensing surface of the at least one cryogenic tube is covered, at least in part, with fins to increase the exchange surface.

5. The regasification device according to claim 1, characterized in that the external condensing surface of the at least one cryogenic tube is covered, at least in part, with a capillary structure on which the working fluid in gaseous phase condenses in a capillary condensation regime.

6. The regasification device according to claim 2, characterized in that it is inside at least one structure with at least one fan, blower or turbine to direct the flow of damp air onto the evaporative surface of the evaporative condenser tubes or chambers.

7. The regasification device according to claim 1, characterized in that it comprises more than one casing with a specific working fluid to work within a specific working temperature range above its solidification temperature.

8. The regasification device according to claim 1, characterized in that it comprises at least one heat pipe inserted between the at least one casing and the at least one hermetic container under vacuum conditions, and because the at least one heat pipe contains a specific two-phase working fluid with a solidification point at a temperature lower than the range of working temperatures of the heat pipe.

9. The regasification device according to claim 8, characterized in that at least one heat pipe incorporates or is connected to a sensitive heat exchanger to control the temperature of the working fluid.

10. The regasification device according to claim 8, characterized in that the at least one interposed heat pipe comprises at least one evaporative tube on its external surface and a condenser on its internal surface that evaporates the working fluid and the evaporated gaseous phase is supplied at a controlled temperature inside the at least one casing, the working fluid being a two-phase working fluid with a solidification point below the temperature of the external surface of the at least one cryogenic tube.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0020] A more detailed explanation is given in the description that follows which is based on the attached figures:

[0021] FIG. 1 shows a longitudinal cross section of a schematic representation of a regasification device,

[0022] FIG. 2 shows a diagram of a regasification device with evaporative condenser chambers inside a container with at least one fan, blower or turbine to drive damp air, and

[0023] FIG. 3 shows a longitudinal cross section of a schematic representation of a regasification device with intermediate heat pipes.

DETAILED DESCRIPTION

[0024] As illustrated in FIG. 1, the regasification device for Liquefied Natural Gas, LNG, and the cogeneration of cold fresh water and cold dry air comprises, at least: [0025] At least one LNG phase change cryogenic tube 3 through which liquefied natural gas LNG 1 is fed at one end and revaporized natural gas 2 is extracted at the other end. The internal surface of this tube is LNG evaporative and the external surface is a condenser. LNG phase-change cryogenic tubes are known and described in the state of the art. They are built of metals and sections appropriate to withstand the temperature differential to which they are subjected. These are tubes that, with the correct external supply of energy, have the capacity to maintain within their walls the thermal gradient between LNG and a controlled temperature on their external surface, as is the case with Open Rack Vaporizers used in LNG regasification and on which seawater at ambient temperature is currently poured. [0026] At least one hermetic casing 4 that withstands vacuum conditions and is traversed by at least one cryogenic tube 3. Inside the at least one casing 4 there is a working fluid under vacuum conditions, part in liquid phase 5 and part in gaseous phase 6. This two-phase 5 and 6 working fluid can be pure water or an aqueous solution or other two-phase working fluid. Given the temperature gradient between the external surface of the at least one cryogenic tube 3 and the temperature of the working fluid in gaseous phase 6, the gaseous phase 6 of the working fluid condenses on the external surface of the at least one LNG tube 3. Upon condensing, the gaseous phase 6 of the working fluid releases energy in the form of latent heat of condensation and sensible heat that is absorbed by the LNG for its regasification process and for increasing the temperature of the natural gas that is generated. The liquid phase 5 of the working fluid accumulates at the bottom of the at least one casing 4. [0027] The working fluid in liquid phase 5 is supplied to the internal evaporative surface of the evaporative condenser tubes or chambers 7 that are outside the at least one casing 4. The evaporative condenser tubes or chambers 7 are under vacuum conditions inside. Since the evaporative condenser tubes or chambers are outside the at least one casing 4, significant savings are achieved in the CAPEX capital cost of the at least one casing 4 and the interior volume of the at least one casing 4 ceases to be a limiting factor of the operating capacity of the device. [0028] A current of damp air 8 that can be driven by at least one fan, blower or turbine 19 flows on the external surface of the evaporative condenser tubes or chambers 7. The water vapor contained in the flow of damp air 8 condenses on the external condensing surface of the evaporative condenser tubes or chambers 7, so that the water vapor condensed on the external surface of the evaporative condenser tubes or chambers 7 releases energy in the form of latent heat of condensation and sensible heat to the working fluid 5 that flows on the internal surface of the evaporative condenser tubes or chambers 7 that evaporates at least in part, generating a gaseous phase 12 that exits through one end of the evaporative condenser tubes or chambers 7. The condensed water 10 resulting from this process of condensation of the water vapor contained in the air flow 8 which is cold after the transfer of energy, flows through the external condensing surface of the evaporative condensers tubes or chambers 7 and accumulates inside an external collection container 11 and can be used as cold condensed water for municipal, agricultural or industrial uses. The flow of damp air 8 that flows through the external condensing surface of the evaporative condenser tubes or chambers becomes a flow of dry and cold air 9 that can be directed and used in refrigeration or air conditioning systems. [0029] The outlet of the evaporative condenser tubes or chambers 7 is connected to a hermetic container 16, which is under vacuum conditions, for collecting fluids, in which the rest of the working fluid in the liquid phase 13 and the gaseous phase of the working fluid 12 evaporated on the internal evaporative surface of the evaporative condenser tubes or chambers 7 accumulate. The vapor 12 of the working fluid evaporated on the internal evaporative surface of the evaporative condenser tubes or chambers 7 is directed 15 to the inside of the at least one casing 4 where it will condense again on the external condensing surface of the at least one cryogenic tube 3. The rest of the liquid phase 13 of the working fluid accumulated inside the container 16 is pumped 14 to the interior of the at least one casing 4.

[0030] The device also includes a regulating system for the flow of LNG 1 that is fed into the cryogenic tube 3 and a regulating system for the flow of damp air 8 that is supplied on the external condensing surface of the at least one condenser-evaporator chamber and/or tube. These LNG and damp air flows must be balanced so that the working fluid remains in the liquid phase and at a controlled temperature. [0031] In order to increase the energy transfer coefficient, the internal evaporative surface of the evaporative condenser tubes or chambers can be covered, at least in part, with a capillary structure in the form of microslots, microgrooves, sintered wick or other capillary structure in which the liquid-gas interface of the working fluid curves and flows orderly within the capillary structure without forming liquid films so that the evaporation occurs in a capillary evaporation regime. Since it is a working fluid without impurities or mineral precipitation problems, there are no risks of blocking the various forms of capillary structures. [0032] In order to increase the energy transfer coefficient, the external condensing surface of the evaporative condenser tubes or chambers can be covered, at least in part, with a capillary structure in the form of microslots, microgrooves, sintered wick, or other capillary structure in which the gas-liquid interface of the condensed water curves and flows orderly within the capillary structure without forming water films, so that condensation occurs in a capillary condensation regime. [0033] In order to increase the energy transfer coefficient, the external condensing surface of the cryogenic tube 3 can be covered at least in part with fins to increase the exchange surface and can be covered at least in part with a capillary structure on which the working fluid condenses in a capillary condensation regime.

[0034] As shown in FIG. 2, one embodiment of the invention consists in arranging the evaporative condenser tubes or chambers 17 inside at least one structure 18 with at least one fan, blower or turbine 19 that drives a flow of damp air 8 on the external evaporative surface of the evaporative condenser tubes or chambers 17.

[0035] As shown in FIG. 3, the regasification device can be made up of more than one casing 4 placed consecutively around at least one cryogenic tube 3 so that inside each casing 4 it is possible to work with a specific range of temperatures and with different working fluids 20, 21 adapted to each temperature range.

[0036] To prevent the formation of ice on the external surface of the at least one LNG cryogenic tube 3, at least one heat pipe 27, 28, 29 can be inserted. The at least one heat pipe 27, 28, 29 can contain different working fluids 20, 22, 23.

[0037] The at least one heat pipe 27, 28, 29 can incorporate an internal or external sensitive heat exchanger 25, 26 to control the temperature of the working fluid 20, 22, 23.

[0038] The at least one heat pipe 27 comprises at least one external evaporative surface and one internal condensing surface 24 that evaporates the working fluid 20 and the evaporated gaseous phase is supplied at a controlled temperature inside the casing 4, the working fluid 20 being a two-phase working fluid with a solidification point below the temperature of the external surface of the at least one cryogenic tube 3, so that the solid phase of the working fluid cannot accumulate on the external surface of the cryogenic tube 3 and the temperature of the gaseous phase of the working fluid that is supplied to the external surface of the cryogenic tube 3 is controlled. Next, n heat pipes 28 can be inserted with their working fluid 22 corresponding to their range of working temperatures and sensitive heat exchange systems 26 to create a progressive gradient of working temperatures in which the working fluid does not solidify.

[0039] At the end of this insertion of at least one heat pipe, the working fluid in liquid phase 23 that is supplied to the internal evaporative surface of the evaporative condenser tubes or chambers 7 on whose external surface the water vapor of the damp air 8 condenses is at a temperature above 0° C. which guarantees that the condensed water on the external surface of each evaporative condenser tube or chamber 7 does not freeze.