FR2927160A1 - Heating and/or cooling method for room in hotel, involves connecting heating device and heat exchanger by delivery and return ducts to form closed loop heat-transfer fluid circuit, where delivery duct has fluid circulation device - Google Patents

Abstract

The method involves installing a heating device (1) on an area to be heated or cooled. A heat exchanger (2) e.g. shell and tube heat exchanger, is immersed at a submarine depth at which the temperature of sea water is at a level, where the exchanger is made of cupronickel. The heating device and the exchanger are connected by a delivery duct (3) and a return duct (4) so as to form a closed loop heat-transfer fluid circuit, where the delivery duct is equipped with a circulation device (5) e.g. pump, to circulate heat transfer fluid that is cooled by melting of another fluid e.g. fatty acid. The fatty acid is chosen from lauric acid, myristic acid and/or stearic acid. An independent claim is also included for a heating and/or cooling device comprising a closed loop heat-transfer fluid circuit.

Description

The present invention relates to a method and apparatus for heating and / or cooling using underwater water as cold source or hot source. It applies in particular, but not exclusively, to the production of a stream of cooled water that can be used to cool rooms. In general, it is known that there are already heating and / or cooling systems using heat exchangers connected to a device for pumping seawater to a marine depth corresponding to a temperature. sought, by means of a pump 20 connected to a pipe partially immersed.

The seawater thus sucked passes into the primary circuit of an exchanger and is then discharged into the sea, preferably at a depth corresponding to its temperature. In passing through this primary circuit, the seawater exchanges heat with the secondary circuit of the heat exchanger, which may for example be connected to an air conditioning installation.

It is also known that the implementation of this solution requires the use of pipes having a minimum diameter, namely generally pipes having at least 60 centimeters of internal diameter. Indeed, the pumping by suction of a liquid in a pipe causes, due to pressure losses, a decrease in the pressure and therefore the vaporization temperature of the liquid, the vaporization temperature of a liquid flowing in a pipe being proportional to the pressure of this liquid. However, the vaporization of the liquid is undesirable, particularly because of the induced cavitation phenomenon which alters the structure of the equipment. Thus, in order to avoid the undesirable vaporization of a liquid circulating in a pipe, pipes having a minimum diameter are used so as to reduce the pressure drops which depend in particular on the friction surface of the liquid with the inner wall of the pipe. .

However, the use of "big" pipes for this type of application has the following disadvantages: • a heavy and expensive infrastructure is required for their transport and / or installation; • They are in the form of bars, generally 12 meters long, which must be welded on site; • their high manufacturing and / or transport and / or installation costs increase the break-even point of the device.

The purpose of the invention is therefore more particularly to eliminate these drawbacks by proposing a method and a device which allow a heat exchange between a heat transfer fluid circulating in a closed circuit and the seawater situated at a depth corresponding to a desired temperature, by example at a depth of 1000 meters at which the temperature of the oceans oscillates on average between 2 and 4 ° C. The use of a forced circulation in a closed circuit makes it possible to push back the "suction limit" which can be defined as the threshold of maximum suction power before which the liquid vaporizes, and therefore to use a For this purpose, the invention proposes a method of heating and / or cooling, characterized in that it comprises the production of a closed loop heat transfer fluid circuit by the implementation the following steps: • the installation of at least one thermal device on the site that it is desired to heat or cool, this thermal device may comprise at least one wind ilo û convector; • immersing at least one heat exchanger at an underwater depth at which the water temperature is at a first level which corresponds to the desired temperature; Connecting the thermal device and the heat exchanger by means of two conduits respectively for supplying and returning a heat-transfer fluid, at least one of said ducts being equipped with at least one circulation device of said coolant. In this way and advantageously, in the closed-loop circuit, a hydrodynamic equilibrium is obtained which makes it possible to push back the "suction limit" and thus to use more "small" supply and return ducts.

Thus, these conduits may have an internal diameter of less than 60 centimeters and preferably of between 10 and 25 centimeters.

The use of "small" ducts of the aforementioned type has the following advantages: • they can be presented in rolls of 100 meters in length, which simplifies their transport and more generally their movement; • they are easier to manipulate by the operators; • they require for their installation nautical means (such as barges 30 goods transport, fishing boats) often present on the installation site and therefore cheap; • the necessary device for the implementation of the process can be installed at a reasonable price, which makes this technology accessible to "average" consumers (such as hotels).

Preferably, the circulating device of said heat transfer fluid is included on or in the descending pipe, namely the duct in which the coolant flows to the immersed heat exchanger.

In addition, advantageously, the implementation of the method according to the invention makes it possible in particular to benefit from the following advantages: the maintenance of this exchanger is extremely reduced or even non-existent; • the exploitation of the invention does not degrade the environment indeed, the solutions of the state of the art require to "clean" periodically the conduits by injecting a chlorine solution which will inevitably end up in the marine environment gold a closed loop avoids this pollution; The installation, operation and maintenance of the invention are simplified. Embodiments of the invention will be described hereinafter by way of non-limiting examples with reference to the accompanying drawings, in which:

Figure 1 is a schematic representation of the device for carrying out the method according to the invention.

FIG. 2 is a schematic representation of the thermal device of the device for implementing the method according to the invention. Figure 3 is a schematic representation according to an alternative embodiment of the invention of the device shown in Figure 1, this device comprising two subsea heat exchangers.

Figure 4 is a schematic representation of a reversible heat pump to which the supply and return conduits of the device according to the invention can be connected.

FIG. 5 is a diagrammatic representation of a submerged heat exchanger which is bypassed by means of a bypass duct controlled by two anti-return valves.

Figures 6.a and 6.b are a schematic representation of a submerged heat exchanger respectively comprising a tubular element and a tubular element associated with a pump.

In the example shown in FIG. 1, the device for carrying out the method according to the invention comprises a closed-loop heat transfer fluid circuit comprising in particular: • a thermal device 1 situated on the site that it is desired to heat or cool. • A heat exchanger 2 may be including but not exclusively of the tube and calender type. In this case, this heat exchanger 2 comprises many metal tubes or a coil in which circulates the heat transfer fluid to be cooled or heated, the tubes or the coil immersed in the seawater in which the exchanger 2 is immersed, which allows to create a thermal contact over a large area between the heat transfer fluid to be cooled or heated and sea water. This heat exchanger 2 in this case is immersed to a depth underwater where the temperature water is at a first level, this temperature being low enough to cause cooling of the heat transfer fluid to a desired temperature, in order to allow efficient operation of the thermal device 1. A supply line 3 and a partially submerged return duct 4, these ducts 3, 4 having in this case a "small" internal diameter, namely, preferably, an internal diameter of less than 60 centimeters. The respective lower end of each of these ducts 3, 4 is connected to said heat exchanger 2 while their respective upper end is connected to the thermal device 1 • At least one circulation device 5 of the coolant, such as a pump, this circulator 5 being included on or in one of said supply ducts 3 or return 4; more precisely, this circulation device 5 of the heat transfer fluid is preferably included on or in the descending pipe so that the coolant is pulsed and not aspirated.

Thus, in the case of a cooling of a site, for example in summer, under the effect of the action of the circulation device 5, the coolant present in the circuit circulates successively: in the thermal device 1 where it absorbs calories from the environment and as a result it heats up (high temperature); • in the return duct 4 in which it is pulsed and where it cools progressively by yielding a fraction of the calories that it has absorbed in the thermal device 1; • in the submerged heat exchanger 2 where it gives up the remaining fraction of the calories that it has absorbed by cooling to reach the desired low temperature (which is very close to the temperature of the seawater at the depth at which the exchanger 2 is immersed); • in the supply duct 3 which can be surrounded by an insulating sheath in order to maintain its internal temperature constant and thus prevent its warming on contact with layers of shallower and therefore warmer seawater.

As shown in FIG. 2, the thermal device 1 may comprise at least one convector fan 1 'connected to an ice-water plant 1 "so as to constitute an ice-water loop 20 connected to said supply ducts and 3, 4 (not shown) More specifically, this thermal device 1 comprises in this case four fan convectors 1 'arranged in parallel, each convector fan 1' being respectively connected at the input and at the output by a d-branch. an upstream duct 21 and a downstream duct 22 of the chilled water loop 20. These upstream ducts 21 and downstream ducts 22 are connected to the inlet and the outlet of said chilled water plant 1 "which makes it possible to maintain or lower the temperature of the water circulating in the loop 20, the latter thus allowing for example to transfer frigories of ice water in the air of a room to be air-conditioned.

Of course, the device according to the invention is not limited to the cooling of a site. Indeed, this device can also be used for warming this site, for example in winter. In this case, as shown in FIG. 3, the return duct 4 may be equipped with a second exchanger 9 located at a depth where the temperature of the water is maximum in winter. The flow direction of the heat transfer fluid will be reversed so as to obtain the following operating cycle: in the thermal device 1, the heat transfer fluid whose temperature is relatively high transfers calories to the ambient environment while cooling; When passing through the duct 3, its temperature can be kept constant by means of an insulating sheath of the aforesaid type; The heat transfer fluid does not pass into the first exchanger 2 which is bypassed by means of a bypass duct 11 controlled by two anti-return valves 12 arranged, as shown in FIG. 5 , respectively at the inlet and the outlet of said bypass duct 11, these valves 12 which are oriented in an opposite direction may be of the spring type; The heat transfer fluid takes a first section 10 of the return pipe 4 leading to the second heat exchanger 9. In this section 10, the temperature of the coolant liquid can be kept substantially constant thanks to the use of an insulating sheath surrounding at least a part section 10; In the second heat exchanger 9, the heat transfer liquid undergoes a heating which brings it to a temperature close to the sea water at the depth II; The heat transfer fluid heated in the second exchanger 9 returns to the thermal device 1 through a section of the return duct 4 (possibly insulated when traveling out of the seawater).

In cooling operation, the circulator 5 will be controlled so as to cause a flow of the fluid in the opposite direction. In this case, thanks to the anti-return valves 12, the coolant will pass into the first heat exchanger 2. By using a branch circuit 11 similar to that fitted to the first heat exchanger 2, the second heat exchanger 9 can be subject to a derivation. An operation similar to that of the embodiment illustrated in FIG. 1 is thus obtained.

In the example illustrated in FIG. 4, the device is coupled to a heat pump 6, of conventional design, comprising a heat-absorption exchanger 7 and a heat-recovery exchanger 8, this heat pump 6 constituting the device 1. Each of these two exchangers 7, 8 comprises a primary circuit 7 ', 8' forming part of the circuit of the heat pump 6 and a secondary circuit 7 ", 8" which can be connected by means of a connection circuit, either to a heating or cooling circuit, either to the supply ducts 3 and return 4 of a closed-loop circuit comprising a circulator 5 and two immersed exchangers 2, 9 of the type of those shown in FIG. 3, possibly provided with circuits bypass 11.

Thus, in the case of a cooling of a site, the supply ducts 3 and return 4 are connected to the secondary circuit 8 "of the heat transfer exchanger 8, the process allowing the cooling then taking place as follows: • said coolant circulates successively: o in the first exchanger 2 where it is cooled o in the supply line 3 o in said secondary circuit 8 "of the heat transfer exchanger 8 where it absorbs the calories returned by the fluid circulating in the circuit: primary 8 'of said exchanger 8; o in the return circuit 4 where it gradually cools; The fluid circulating in the circuit of the heat pump 6 circulates successively: in the primary circuit 8 'of the exchanger 8 where it restores its calories to said coolant in order to reach a low temperature; o in the primary circuit 7 'of the absorption exchanger 7 calories where it absorbs the calories of a fluid flowing in the corresponding secondary circuit 7 "which can be connected to a cooling circuit.

On the other hand, in the case of a reheating of a site, the supply and return ducts 4 and 4 are connected to the secondary circuit 7 "of the heat-absorption exchanger 7, the process allowing the heating to take place. then performing as follows: • said heat transfer fluid circulates successively: o in the second heat exchanger 9 where it is heated o in the return pipe 4 2927160 -10- o in said secondary circuit 7 "of the heat exchanger 7 d absorption of calories where it yields its calories to the fluid circulating in the primary circuit 7 'of said exchanger 7; o in the supply circuit 3; • the fluid flowing in the circuit of the heat pump 6 circulates successively: o in the primary circuit 7 'of the exchanger 7 where it absorbs the calories transported by said heat transfer fluid; o in the primary circuit 8 'of the refund exchanger 8 of 10 calories where it restores its calories to a fluid flowing in the corresponding secondary circuit 8 "which can be connected to a heating circuit.

Advantageously and preferentially, said first and second heat exchangers 2, 9 do not comprise moving parts, their maintenance thus being almost non-existent.

In addition, it is known that the demands of heat and cold production vary according to the seasons, the climatic conditions, but also the hours of the day. Thus, there are peaks and troughs of consumption.

In order to respond satisfactorily to these variations in demand, it is possible to use: a heating and / or cooling device according to the invention, shaped and dimensioned so as to be able to respond to consumption peaks, and that works in degraded mode the rest of the time; or a heating and / or cooling device according to the invention, shaped and dimensioned so as to be able to respond to an average consumption, this heating and / or cooling device comprising a frigory storage system; to cope with the peaks of demand.

Preferably, said cold storage system may have the following characteristics: it is dimensioned so as to be able to provide at least one third of the cold production requirements during a hot day; • its heat insulation is calculated so that it does not lose more than 10% of cooling capacity per 24-hour period; Its storage capacity is substantially equal to 500 kWh.

According to an alternative embodiment of the invention, this storage device may consist of a reservoir of a fluid such as water, the temperature of which is lowered by using the excess night cold, the icy water thereof. tank being used to meet peaks of daytime demands for cold production.

According to this alternative embodiment of the invention, this reservoir is preferably divided into horizontal strata by means of semi-permeable plates in order to allow the water contained in this reservoir to be distributed in stratified layers, each layer having a level of the predetermined temperature and the coldest layers remaining in the lower part of the tank, the latter being connectable to said thermal device 1. The coldest layers of this tank may for example be fed with pumped water, preferably at night, in the underwater depths.

According to another alternative embodiment of the invention, this storage device may consist of a tank disposed on the surface and comprising a fluid whose solidification temperature is within a determined range, for example between 8 ° and 10 ° C. In this way, the passage of a stream of chilled water 2927160 - 12 - in this tank, whose temperature is below this solidification temperature (for example, a temperature close to 0 ° C.), makes it possible to cause a solidification of said fluid, this phase change resulting in a heat recovery which is substantially proportional to the mass and the latent heat of solidification of the fluid. Thus, the flow of water at the outlet of the reservoir will be warmed by this return of heat resulting from the solidification of said fluid.

Conversely, the passage of a stream of heated water in this tank, whose temperature is higher than said solidification temperature (for example, a temperature of 10 ° C.), makes it possible to cause a melting of said fluid, this phase change resulting in heat absorption which is substantially proportional to the mass and the latent heat of fusion of the fluid. Thus, the flow of water leaving the reservoir will be cooled by this heat absorption resulting from the melting of said fluid.

In this way, by way of non-limiting example, in the case where it is desired to cause a solidification of said fluid included in the reservoir, it will be possible to connect the supply duct 3 and the return duct 4 of the fluid circuit 20. coolant respectively at the inlet and outlet of said tank, the coolant present in the circuit then circulates successively: • in the return duct 4 in which it is pulsed and where it gradually cools; • in the submerged exchanger 2 where it gives up the remaining fraction of the calories which it absorbed while cooling to reach the desired low temperature; In the supply duct 3 which can be surrounded by an insulating sheath in order to keep its internal temperature constant; • in said tank where its low temperature makes it possible to cause at least partial solidification of the fluid in said tank, the heat transfer fluid thus being heated; 2927160 - 13 - • in the return duct 4 or in the thermal device 1 of the aforementioned type.

Thus, this operation is particularly conducive at night in fact, the coolant 5 flowing in the supply duct 3 is colder, which thus allows to cause the solidification of the fluid included in the reservoir.

Still as a nonlimiting example, during the day, the direction of circulation of the heat transfer fluid can be reversed so that it flows successively: • in the supply duct 3; In the first exchanger 2 or preferentially in the second exchanger 9 where its temperature is brought to a temperature close to the level of the seawater to which the exchangers 2, 9 are immersed; In the return duct 4; • in said tank where its temperature allows to cause at least partial melting of the fluid in the tank, the heat transfer fluid thus being cooled; • in the supply duct 3 or in the thermal device 1 of the aforementioned type 20.

In this way, the melting of the fluid included in the reservoir makes it possible to cool the heat-transfer fluid, this reservoir which can be connected to said thermal device 1 thus constitutes an immediately available reserve of frigories, this reserve being able to be exploited to cope with a peak cold demand.

Obviously, the heat transfer fluid circuit may comprise a bypass circuit that may be provided with valves or valves, which allows the heat transfer fluid to bypass the passage in said reservoir when it is not deemed necessary to have a reserve of frigories. By way of non-limiting example, said fluid may be included in the reservoir, may be a fatty acid of general formula CH 3 - (CH 2) n - COOH (where n is from 2 to 16), such as in particular lauric acid, myristic acid, stearic acid, or a mixture of fatty acids to set the melting temperature at a certain value (s).

In addition, the latent heats of the various fatty acids are distributed over a relatively large interval of a thermometric scale. Thus, in the case where said fluid is a mixture of fatty acids, the solidification or melting will be carried out gradually: for example, each fatty acid participating in said mixture will change state depending on its temperature In this manner, the solidification of the fatty acids will gradually solidify during the change of state process by a pasty state allowing it to conform to the shape of the reservoir.

Furthermore, preferably, each exchanger 2, 9 is made of cupronickel (CuNi 10) and is of tubular type, this exchanger 2,9 then comprising an array of substantially parallel tubes shaped and arranged so as to allow the coolant to circulate more slowly than in the supply duct 3 and return 4. which results in an increase in the heat exchange time between the coolant and the seawater in which the exchanger 2, 9 is immersed .

By way of nonlimiting example, preferably, a type 2 exchanger 9 may have a structure to obtain the following results: • the velocity of circulation of the coolant in the exchanger 2, 9 is 1 meter per second; The output flow rate of exchanger 2, 9 is 30 m 3 per hour; The ratio between the volume of the exchanger 2, 9 and the volume of the internal piping is 50 to 1; 2927160 - 15 - • the temperature (in degrees Celsius) of the coolant at the outlet of the exchanger 2, 9 is substantially equal to the temperature of the ambient medium in which the exchanger 2, 9 is immersed to which is added 0, 5 ° C. Advantageously, according to an alternative embodiment of the invention, as shown in Figure 6.a, the exchanger 2, 9 may be "controlled convection". Thus, this exchanger 2, 9 may comprise a tubular element 30, in this case vertically oriented, in the interior of which coaxially extend the metal tubes or the coil of said exchanger 2, 9.

In this way, natural convection is favored by creating a movement (in the ascending species) of the fluid in which the metal tubes or the coil are immersed, namely in the case of seawater, which allows 15 to optimize the energy efficiency of said exchangers 2, 9.

Advantageously, as shown in Figure 6.b, the exchanger 2, 9 immersed may be "forced convection" and then further comprises a means such as a circulation pump 31 which optimizes Even more the energy efficiency of said exchangers 2, 9.

Each exchanger 2, 9 can thus be of the "natural convection" type, or "controlled convection", or "forced convection" type. In addition, each exchanger 2, 9 can be hybridized and consist of the combination of several of said exchanger types 2, 9.

Claims (24)

claims 1. A method of heating and / or cooling, characterized in that it comprises the realization of a heat transfer fluid circuit 5 in a closed loop by the implementation of the following steps: • the installation of at least one device thermal (1) on the site that it is desired to heat or cool; • immersing at least one heat exchanger (2) at an underwater depth at which the water temperature is at a first level; Connecting the thermal device (1) and the exchanger (2) via two supply ducts (3) and return ducts (4), at least one of said ducts (3, 4) being equipped with at least one circulation device (5) for a heat transfer fluid. 15 2. Heating and / or cooling device for implementing the method according to claim 1, characterized in that it comprises a closed loop heat transfer fluid circuit comprising a thermal device (1) located on the site that the It is desired to heat or cool, this thermal device (1) being connected to at least one heat exchanger (2) immersed to an underwater depth at which the water temperature is at a first level, by the intermediate of two conduits respectively supply (3) and return (4), at least one of said conduits (3, 4) being equipped with a circulation device 25 (5) of the coolant. 3. Device according to claim 2, characterized in that the heat exchanger (2) is of the tube and calender type. 2927160 -17- 4. Device according to one of claims 2 and 3, characterized in that the supply duct (3) and / or the return duct (4) is at least partly covered with a thermally insulating sheath. 5. Device according to one of claims 2 to 4, characterized in that the return duct (4) is equipped with a second exchanger (9). 6. Device according to one of claims 2 to 5, characterized in that the closed loop heat transfer fluid circuit comprises at least one bypass duct (11) controlled by two anti return valves (12) respectively disposed to the inlet and outlet of said bypass duct (11), these valves (12;) which are oriented in an opposite direction may be of the spring type. 7. Device according to claim 6, characterized in that the closed loop heat transfer fluid circuit comprises two bypass ducts (11) which respectively enable the first exchanger (2) and the second exchanger (9) to be derived. 8. Device according to one of claims 2 to 7, characterized in that in the case of a cooling of a site under the effect of the circulation device (5), the heat transfer fluid present in the circuit circulates successively: • in the thermal device (1) where it absorbs calories from the environment and consequently it heats up; • in the return duct (4) where it cools progressively by yielding a fraction of the calories that it has absorbed in the thermal device (1); In the exchanger (2) where it gives up the remaining fraction of the calories which it has absorbed while cooling to reach the desired low temperature which corresponds substantially to the temperature of the sea water at the depth to which exchanger (2) is immersed; • in the supply duct (3) which can be surrounded by an insulating sheath in order to keep its internal temperature constant and thus prevent its heating in contact with layers of shallower and therefore warmer seawater. 9. Device according to one of claims 6 and 7, characterized in that in the case of a warming of a site under the effect of the circulation device (5), the direction of circulation of the heat transfer fluid is reversed. in order to obtain the following operating cycle: in the thermal device (1), the coolant whose temperature is relatively high yields calories to the ambient environment while cooling; When passing through the supply duct (3), its temperature can be kept constant by means of an insulating sheath of the aforesaid type; • the coolant does not pass into the first exchanger (2) which is bypassed through a bypass duct (11) controlled by two check valves (12); 20 the heat transfer fluid borrows a first section (10) of the return duct (4) leading to the second exchanger (9); in this section (10), the temperature of the coolant liquid can be kept substantially constant through the use of an insulating sheath surrounding at least a portion of the section (10); In the second heat exchanger (9), the coolant undergoes a warming which brings it to a temperature close to seawater at the depth (I1); The heat transfer fluid heated in the second exchanger (9) returns to the thermal device (1) through a section of the return duct (4). 30 2927160 - 19- 10. Device according to one of claims 6 to 9, characterized in that in cooling operation, the circulator (5) is controlled so as to cause a flow of the fluid in the opposite direction; in this case, thanks to the anti-return valves (12), the coolant 5 will pass into the first exchanger (2); the second exchanger (9) being derivable by using a branch circuit (11) similar to that fitted to the first exchanger (2). 11. Device according to one of claims 2 to 10, characterized in that it is coupled to a heat pump (6) of conventional design comprising a heat-absorbing exchanger (7) and a heat exchanger (8). ) calorie recovery, this heat pump (6) constituting said thermal device (1); each of these two exchangers (7, 8) comprises a primary circuit (7 ', 8') forming part of the circuit of the heat pump (6) and a secondary circuit (7 ", 8") which can be connected by means of a connection circuit, either to a heating or cooling circuit, or to the supply (3) and return (4) conduits of a closed-loop circuit comprising a circulator (5) and two submerged exchangers (2, 9) possibly provided with bypass circuits (11). 20 12. Device according to claim 11, characterized in that in the case of a cooling of a site, the supply ducts (3) and return (4) are connected to the secondary circuit (8 ") of the heat transfer exchanger (8), the process allowing the cooling then taking place as follows: said heat transfer fluid circulates successively: in the first heat exchanger (2) where it is cooled; fed (3) o in said secondary circuit (8 ") of the exchanger (8) 30 calorie recovery where it absorbs the calories returned by the fluid flowing in the primary circuit (8 ') of said exchanger (8); In the return circuit (4) where it cools progressively; The fluid circulating in the circuit of the heat pump (6) circulates successively: in the primary circuit (8 ') of the heat exchanger (8) where it restores its calories to said coolant in order to reach a low temperature; o in the primary circuit (7 ') of the heat absorption exchanger (7) where it absorbs the calories of a fluid flowing in the corresponding secondary circuit (7 ") which can be connected to a cooling circuit. 13. Device according to claim 11, characterized in that in the case of a warming of a site, the supply ducts (3) and return (4) are connected to the secondary circuit (7 ") of 15 l heat exchange exchanger (7), the process allowing the heating then taking place in the following manner: said heat transfer fluid circulates successively: in the second heat exchanger (9) where it is heated; return (4) 20 o in said secondary circuit (7 ") of the heat-absorbing exchanger (7) where it transfers its calories to the fluid circulating in the primary circuit (7 ') of said exchanger (7); o in the supply circuit (3); The fluid flowing in the circuit of the heat pump (6) circulates successively: in the primary circuit (7 ') of the exchanger (7) where it absorbs the calories transported by said heat transfer fluid; in the primary circuit (8 ') of the heat transfer exchanger (8) where it restores its calories to a fluid circulating in the corresponding secondary circuit (8 ") which can be connected to a heating circuit. 2927160 -21- 14. Device according to one of claims 2 to 10, characterized in that the thermal device (1) comprises at least one convector fan (1 ') connected to an ice-water plant (1 ") in order to constitute a 5 an ice-water loop (20) connected to said supply and return ducts (3, 4), which thermal device (1) comprises fan convectors (1 ') arranged in parallel, each convector fan (1') being respectively connected at the inlet and at the outlet by a branch of an upstream duct (21) and a downstream duct (22) of the chilled water loop (20), these upstream (21) and downstream (22) ducts are connected to the inlet and the outlet of said chilled water plant (1 ") which makes it possible to maintain or even lower the temperature of the water circulating in the loop (20), the latter thus making it possible, for example, to transfer frigories of icy water in the air of a room to be air conditioned. 15. Device according to one of claims 2 to 14, characterized in that the supply ducts (3) and return (4) have an internal diameter of less than 60 centimeters. 16. Device according to one of claims 2 to 15, characterized in that it comprises a system for storing frigories. 17. Device according to claim 16, characterized in that the storage device consists of a reservoir of a fluid such as water, whose temperature is lowered by using excess cold night, the ice water of the reservoir being used to meet peaks of daytime demands for cold production; this tank is divided into horizontal strata by means of semi-permeable plates in order to allow the water contained in this reservoir to be distributed in stratified layers, each layer having a determined temperature level and the coldest layers; remaining in the lower part of the tank, the latter being connectable to said thermal device (1). 18. Device according to claim 16, characterized in that said storage device consists of a reservoir disposed on the surface and comprising a fluid whose solidification temperature is within a determined range; in this way, the passage of a stream of chilled water in this tank, the temperature of which is below this solidification temperature, makes it possible to cause solidification of said fluid, this phase change resulting in a substantially proportional return of heat. the mass and the latent heat of solidification of the fluid; thus, the flow of water at the outlet of the tank will be warmed by this return of heat resulting from the solidification of said fluid; conversely, the passage of a stream of heated water in this tank, the temperature of which is higher than said solidification temperature makes it possible to cause a melting of said fluid, this phase change resulting in a heat absorption which is substantially proportional to the mass and the latent heat of fusion of the fluid; thus, the flow of water out of the tank will be cooled by this absorption of heat resulting from the melting of said fluid. 19. Device according to claim 18, characterized in that: • in the case where it is desired to cause solidification of said fluid 25 included in the reservoir, the supply duct (3) and the return duct (4) of the heat transfer fluid circuit are respectively connected to the inlet and the outlet of said tank, the coolant present in the circuit then circulates successively: o in the return pipe (4) in which it is pulsed and where it cools gradually ; In the immersed heat exchanger (2) where it gives up the remaining fraction of the calories which it has absorbed while cooling to reach the desired low temperature; o in the supply duct (3) which can be surrounded by an insulating sheath in order to keep its internal temperature constant; o in said tank where its low temperature makes it possible to cause at least partial solidification of the fluid in said tank, the coolant being thus heated; o in the return duct (4) or in the thermal device (1) of the aforementioned type; During the day, the direction of circulation of the coolant is reversed so that the latter circulates successively: in the supply duct (3); o in the first exchanger (2) or in the second exchanger 15 (9) where its temperature is brought to a temperature close to the level of the seawater to which the exchangers (2, 9) are immersed; o in the return duct (4); o in said tank where its temperature makes it possible to cause at least partial melting of the fluid included in this tank, the heat transfer fluid thus being cooled; o in the supply duct (3) or in the thermal device (1) of the aforementioned type; in this way, the melting of the fluid included in the reservoir makes it possible to cool the heat-transfer fluid, this reservoir which can be connected to said thermal device (1) thus constitutes an immediately available reserve of frigories, this reserve being able to be exploited to cope with a peak of cold demand. 5 10- 24 - 20. Device according to one of claims 18 and 19, characterized in that the heat transfer fluid circuit comprises a bypass circuit which allows the heat transfer fluid to bypass the passage in said tank when it is not considered necessary to have a reserve of frigories. 21. Device according to one of claims 18 to 20, characterized in that the fluid can be included in the reservoir, is a fatty acid of general formula CH3 - (CH2) n - COOH (where n is from 2 to 16) , such as in particular lauric acid, myristic acid, stearic acid, or a mixture of fatty acids for setting the melting temperature at a determined value (s). 22. Device according to one of claims 2 to 21, characterized in that each exchanger (2, 9) is made of cupronickel (CuNi 10) and is of tubular type, this exchanger (2,9) then comprising a network of substantially parallel tubes shaped and arranged to allow the heat transfer liquid to circulate more slowly than in the feed duct (3) and return (4), which results in an increase in the heat exchange time between the fluid coolant and seawater in which the exchanger (2, 9) is immersed. 23. Device according to one of claims 5 to 22, characterized in that the exchanger (2, 9) comprises a tubular element (30) in the inner space of which extend the metal tubes or the coil 25 of said exchanger (2, 9). 24. Device according to claim 23, characterized in that the exchanger (2, 9) comprises a means such as a circulation pump (31). 30