FR2781563A1 - METHOD FOR TRANSFERRING THERMAL ENERGY FROM A FLUID AND INSTALLATION IMPLEMENTING SAID METHOD - Google Patents

Abstract

The method involves feeding the hot liquid into a container (20) under low pressure to vaporize it and cool the remaining liquid. The vapor is fed to a second container for extraction of the hot gas. The first and second containers are connected by two connecting circuits which are operated repetitively to feed the material to the second container.

Description

METHOD FOR TRANSFERRING THERMAL ENERGY FROM A

  FLUID AND INSTALLATION IMPLEMENTING THIS PROCESS

  The present invention relates to a process for transferring thermal energy in recovery of a vaporizable fluid. It also relates to an installation implementing this process. The invention can find application in numerous fields, and in a practical manner whenever it is desired to cool a hot or lukewarm fluid, such as water, milk, various fruit juices, chemical solutions, etc. However, in what follows, to fix the ideas, we will consider that the fluid in question is water. Even more particularly, we will first consider the case of an industrial installation discharging hot, or at least lukewarm, waste water which cannot be reused and which is sent to

  sewage treatment plants, or even towards rivers.

  It is easily understood that it is advantageous to recover the maximum number of calories possible from these effluents. Generally, this recovery is carried out by using the effluents to heat other products via a traditional heat exchanger in which the heat transfer takes place through a material wall. However, the yield is not optimum and the temperature obtained from the reheated product is not

very high.

  It is also known that, in many installations (nuclear power plants, etc.), steam condensers are used which consume a large amount of cooling water. This then carries a very large amount of calories. The water resulting from the condensation is generally recycled after being cooled in what is known as an atmospheric cooling tower, since the cooling flow is released by exhaust into the atmosphere. In almost all cases, calories are therefore released into the atmosphere, and consequently lost. It would therefore also be interesting to recover these calories. Finally, in the known art, it is also customary, under certain circumstances, to recover the fluid in the vapor phase, for example water vapor. This water vapor is then obtained by compressing the vaporized part of the heated primary fluid. However, this compression is usually carried out by using centrifugal machines which do not make it possible to obtain a pressure

  absolute equal to or greater than atmospheric pressure.

  The object of the invention is in particular to propose a heat transfer process, with energy recovery, from a vaporizable fluid. This process can involve either the recycling of the liquid fluid after cooling, or the recycling of the fluid in the gaseous phase, or else offer these two in combination

recycling possibilities.

  To do this, a device allowing the implementation of the process which is the subject of the invention comprises two enclosures. A fluid is injected into a first enclosure,

  which can be called primary, in liquid and hot phase.

  A fraction of it is vaporized, which causes vacuum and cooling. The fraction of the vaporized liquid is transferred to a second enclosure to be compressed there. The member allowing the transfer is essentially constituted by a cylinder communicating with the two enclosures and provided with a double-acting piston and

  intake and exhaust valves.

  The piston contributes to obtaining the vacuum in the first enclosure and allows fluid compression in

  gas phase transmitted in the second enclosure.

  According to the main characteristic of the process of the invention, the thermal energy is therefore extracted from the primary fluid by transfer of a mass of the fluid, in phase

  gas, from the first enclosure to the second enclosure in which this fluid, still in the gaseous phase, is compressed.

  We can therefore recycle the cooled liquid and, after heating, recirculate it in the first enclosure (primary fluid, in liquid phase). you can also use the compressed steam in the second enclosure

  (secondary fluid, gas phase).

  The process is iterative. After an initial period, an equilibrium is obtained, except for losses. It is sufficient to provide a simple addition of primary fluid and / or

secondary, depending on the application.

  The reciprocating movement of the piston in the cylinder ensuring communication between the two chambers is obtained by a rod-and-crank system driven by a motor,

  advantageously at variable speed.

  In an alternative embodiment, the device

  implementation includes stages arranged in cascade.

  The subject of the invention is therefore a method of cooling a vaporizable utility fluid with recovery of thermal energy, characterized in that it comprises at least the following repetitive steps: introduction of said fluid into a first enclosure and vaporization under vacuum d 'A fraction of this fluid, so as to obtain the cooling of the fraction of non-vaporized fluid and its recovery in the liquid phase; - evacuation of said first enclosure of said fluid in the cooled liquid phase; transfer of said fraction of vaporized fluid to a second enclosure, by means of mechanical coupling means sucking the vaporized fluid out of the first enclosure and discharging it, in the gas phase with a determined compression rate, into said second enclosure; - And evacuation from this second enclosure of said compressed fluid in the gas phase, so as to obtain

  said recovery of thermal energy.

  The invention also relates to an installation for implementing this method. The invention will be better understood and other characteristics and advantages will appear on reading.

  the description which follows with reference to the appended figures,

  among which: - Figures 1A and 1B schematically illustrate the operation of a device for implementing the method according to the invention, in two operating states; - Figure 2A schematically illustrates the application of a device according to the invention to an industrial installation requiring the cooling of a large body of water; - Figure 2B schematically illustrates a condenser used in an industrial installation of the type described in Figure 2A; - Figures 3A and 3B illustrate a practical embodiment of a device according to the invention, comprising several stages; - And Figure 4 illustrates a device of this type, according to an additional embodiment allowing

  to obtain a gas phase fluid under high pressure.

  The method according to the invention will now be described with reference to FIGS. 1A and 1B. These figures schematically illustrate an exemplary embodiment

  of a device allowing the implementation of this process.

  The device 1 essentially comprises three parts: two tanks 2 and 3 and a fluid transfer member 4 making it possible to communicate the chambers, 20 and 30, of the two tanks, 2 and 3, according to methods which go

be explained below.

  The tank 2 receives, in an upper zone, and by a pipe symbolized by the solid line 21, a fluid in the liquid state, which will be called primary. To fix the ideas, we will assume that it is hot water, or at least lukewarm. This water comes from an installation in

  downstream (not shown), an example of which will be given below.

  It is generally necessary to pump water from its place of production. A pump 210 has been provided for this purpose.

  and is arranged on the arrival line 21.

  Inside the enclosure 20 of the tank 2, we

  provides a spray nozzle 22 or the like.

  The sprayed water 23 will be found in the bottom of the enclosure 20. However, part of the mass of water injected into the enclosure 20 will undergo a phase change, and will end up in the form of water vapor 23 ', at a reduced pressure compared to atmospheric pressure, that is to say compared to the pressure prevailing at

outside of enclosure 20.

  By this process, the fraction of non-vaporized water 23 will be able to be recovered, cooled due to the expansion suffered, in the bottom of the enclosure 20. It can therefore be extracted from the enclosure 20, either for reuse and re-inject it through the input circuit 21, after reheating, either to reject it, but at low temperature. The discharge pipe 26 is symbolized by a simple solid line. There is on this pipe 26 an extraction system 6 comprising, for example, a pump 60

and a non-return valve 61.

  As indicated, the enclosure 30 of the second tank 3 communicates with the enclosure 20 of the first tank 2, by means of a fluid transfer member. This comprises a cylinder 40 in which a double-acting piston 41 circulates, and of course a set of pipes allowing a double transfer: a first transfer from the first enclosure 20 to the cylinder 40, and a second transfer from this cylinder 40 to the second

pregnant 30.

  The piston 41 divides, at any time during its travel, the internal enclosure of the cylinder 40 into two chambers, upper 400 and lower 401. The upper chamber 400 communicates with the upper part of the first enclosure 20, by a first pipe 24 and an intake valve 42, disposed at the inlet of the upper chamber 400, and with the upper part of the enclosure 30, by a second pipe 31 and an exhaust valve 43 at the outlet of the upper chamber 400. Similarly, the lower chamber 401 communicates with the lower part of the first enclosure 20, via a third pipe 25 and an inlet valve 44, disposed at the inlet of the lower chamber 401, and with the lower part of the enclosure 30, by a fourth pipe 32 and an exhaust valve 45 at the outlet of the lower chamber 401. The set of intake and exhaust valves requires a unidirectional fluid transfer from the first enclosure 20 to the second

pregnant 30.

  The piston 41 is driven by machinery 5, comprising a motor (not shown) in turn driving a flywheel 50. The flywheel 50 is mechanically coupled to the piston 41 by a conventional assembly "connecting rod 52 and crank 51", connected by an axis 510, so that the piston 41 goes back and forth inside

the enclosure of the cylinder 40.

  FIG. 1A shows a phase of the cycle for which the piston 41 is pulled down, the

  valves 42 and 45 open and valves 43 and 44 closed.

  In this state, the water vapor 23 ′, under reduced pressure, is sucked in by the piston 41 and enters the upper chamber 400, via the line 24 and the lumen of the intake valve 42, which contributes to creating a depression in the enclosure 20. On the other hand, the content of the lower chamber 401, that is to say as will be described below, the water vapor sucked in during the previous cycle, is expelled towards the enclosure 30 by the downward movement of the piston, via the

  exhaust valve light 45 and line 32.

  This expulsion is carried out under pressure, because the movement of the piston 41 is accompanied by compression of the

  gas phase content of the lower chamber 401.

  In FIG. 1B, a phase of the cycle has been shown for which the piston 41 is pushed upwards, the valves 43 and 44 open and the valves 42 and 45 closed. It is an entirely dual state from that described with reference to FIG. 1B. The process and the effects obtained are quite similar to those which have just been described, with the only exception that the upper chamber 400 plays the role of the lower chamber 401, and vice versa. It follows

  that it is the lines 25 and 31 which become active.

  So that the pipe 25 does not suck the liquid at the bottom of the tank 23, it is necessary that it opens into the enclosure 20 at an appropriate level. Likewise, the shape of its mouth must be provided so as not to receive a direct flow of liquid, by spraying. It is possible, to do this, to give it a whistle shape, the bevelled part of which faces downwards, as suggested by the

  Figures 1A and 1B, or a similar form.

  The enclosure 30 comprises an outlet pipe 33, or secondary circuit, advantageously located in the lower zone of this enclosure, for collecting any condensate. This pipe 33 is also advantageously provided with a drain 34 making it possible to remove these condensates. The water vapor 23 ′ (or more generally the fluid in the gaseous phase) extracted from the enclosure 20 is transferred into the enclosure 30. It is found in this enclosure, 5 always in gaseous form, but at a pressure higher

  as the pressure prevailing in the enclosure 20.

  Depending on the specific application, the water vapor 23 "present in the enclosure 30 can either be ejected at atmospheric pressure, if the outlet pipe 33 is open, or available under pressure for use.

  later (upstream installation not shown).

  To fix ideas, and without this limiting in any way the scope of the invention, we will now give a numerical example relating to a practical embodiment of the device according to the invention. The tanks, 2 and 3, are advantageously produced by taking advantage of current techniques in the field of boilermaking and by using standard size sheets. Under these conditions, the tanks are advantageously cylindrical and have upper and lower curved parts. The diameter of the enclosure is 480 mm and the height 1.5 m. The diameter of the pipes 24, 25, 31 and 32 is typically 200 mm. The tanks, 2 and 3, must be watertight and withstand pressures of the order of magnitude of atmospheric pressure. The diameter of the enclosure of the piston 41, and therefore of the enclosure of the cylinder 40, is

  630 mm, and the height of this enclosure is 610 mm.

  We will now describe an example of an industrial installation using a device according to the invention for cooling water, with reference to FIGS. 2A and 2B. The industrial installation shown in FIG. 2A essentially comprises three parts: a boiler room Ch producing steam, a factory U in which this steam is used and a device 1 according to the invention. FIG. 2A shows only the elements necessary for a good understanding of the invention. The elements common to the previous figures bear the same

  references and will only be re-described as necessary.

  The Ch boiler room is of a completely classic type and it is not necessary to describe it further. The steam is transmitted to the factory U by one or more supply lines Ce and the condensates are returned to the boiler room Ch by one or more evacuation lines Cs. Factory U includes a number of

  machines or devices using the steam produced.

  In the example described, the steam supplies a battery of condensers Cl to Cn, arranged in cascade, n being a number

  arbitrary that depends on the specific application.

  FIG. 2B schematically illustrates the structure of a conventional condenser, referenced 7. This receives steam by a supply pipe 70 and the condensates are returned by a pipe 71. Cold water is introduced into the condenser 7 by a supply pipe 73, circulates in the condenser 7 and, by heat exchange with the steam which also circulates, heats up and exits through the pipe 72. For example, in a conventional installation of the known art , the temperature of the water in line 73 is of the order of 20 to 25 ° C. (ambient temperature of the external medium: atmosphere, river water, etc.). It typically comes out at a

temperature of 40 C.

  In the example illustrated in FIG. 2A, the

  condensers Cl to Cn are all similar to condenser 7.

  To fix the ideas, we will consider that the temperature of the vapor in the pipe Ce (entering the condenser C1) is at a temperature of 75 C and enters the last condenser, for example C4, if n = 4, at a temperature of 40 C. Taking into account that the heat exchanges are not perfect, the water leaving this condenser C4, that is to say the water circulating in line 21, is typically at a temperature of order of 40 C. This must be cooled, whether

recycled or not.

  In an installation according to the known art, a cooling tower is used for this purpose, with the drawbacks specific to this type of installation, and which have been previously recalled. The cooling tower, or any similar installation, is advantageously replaced by a device 1 according to the invention, as illustrated

in Figure 2A.

  The operation of this device 1 is identical to what has been described with reference to FIGS. 1A and 1B, and it is unnecessary to repeat it in detail. The hot water, at the outlet of the condenser bank, C1 to Cn, is introduced into the enclosure 20 of the tank 2, where it is vaporized at 22. The remaining liquid part 23, at low temperature, is returned to the condensers, Ci to Cn, using the recycling members 6 (FIGS. 1A and 1B:

  pump 60 and non-return valve 61), via line 26.

  The part of the sprayed water (at 22) transforming into water vapor 23 'is transferred into the enclosure 30 of the second tank 3, under a pressure higher than the pressure prevailing in the enclosure 20. its temperature also rises. The 23 "steam can then be recycled and re-injected at the inlet of the

condensers, Cl to Cn.

  Due to the losses due to vaporization (at 22), it is necessary to provide a top-up of water in the recirculation circuit (line 26). This additional water is provided by an additional pipe 27, connected to the pipe 26, at a first end, and to a water distribution point at low temperature (not shown),

at a second end.

  The machinery 5 for driving the piston 41 is mechanically coupled to a motor 8, for example an electric motor. To fix the ideas, we will now give a numerical example relating to an installation of

typical water cooling.

  It is assumed that the flow rate of the water entering the tank 2, via line 21, is 30,000 l / h and that its temperature is, as previously indicated, 40 C. It can be obtained by the spraying process and expansion, in cooperation with the action of the fluid transfer member 4, a lowering of the temperature of the incoming liquid which is such that the temperature of the liquid 23, recovered in the bottom of the tank 2, that is to say that is to say also the liquid emerging through line 26 and recycled, ie typically of the order of 15 C. It can be seen that this temperature no longer depends on the ambient conditions, as would be the case for a cooling tower, and that we can drop significantly below temperatures

common from 20 to 25 C.

  The pressure prevailing in the enclosure 20 is much lower than atmospheric pressure, ie 0.017 atm (or 1.72 kPa) for the aforementioned conditions. Under these same conditions, taking into account the temperature difference obtained, the quantity of calories released is

  30,000 x (40-15) = 750,000 kcal (or 179,135 kJ).

  The enthalpy of water vapor at 15 C being equal to 588.8 kcal / kg, the quantity of steam produced per hour is

  therefore equal to (750,000 / 588.8), or 1,273 kg / h.

  It is therefore necessary to make a backup

  water equivalent in the return circuit (line 26).

  This make-up, of 1,273 l / h, is brought in via line 27.

  the vaporized water 23 ′ will be found in the enclosure 30 of the tank 3, still in the form of vapor, but under a pressure close to atmospheric pressure, that is to say a pressure much greater than the pressure prevailing in enclosure 20 (i.e. 0.017 atm). In addition, the temperature of the water vapor 23 "in the enclosure 30 rises and can reach values typically between 75 and 100 C. This steam 23" can therefore be recycled by re-injection at the inlet of the plant U (line Ce), via line 33. It is assumed, in fact, that the boiler Ch produces steam at a temperature of 75 C, under a pressure of 0.39 atm

  (i.e. 39.5 kPa). After an initialization period,

  that is to say when the cruising speed is reached, with the losses nearly compensated by a production of steam by the boiler Ch, the recovered steam can be sufficient to supply the factory U. A numerical example concerning the dimensions of the main constituent organs of device 1 has already been given. By keeping these numerical values and the numerical values specified above, the piston 41 must be driven at a speed of 2 revolutions per second. The drive motor 8 should develop a power of the order of 100 kW. To do this, you can select a motor

115 kW standard electric.

  It can easily be seen, in this application example, that the device 1 implementing the method according to the invention is very advantageous. It naturally allows the water to be cooled, but it also allows its recycling and the recovery of the steam produced, therefore also of calories which would otherwise be wasted. Indeed, a conventional cooling tower according to known art rejects

vapor in the atmosphere.

  The device 1, as it has been more particularly described with reference to FIGS. 1A and 1B, is suitable for installations of low or medium power. The word "power" is understood here in terms of the flow of water to be treated per unit of time, or more generally of useful fluid circulating in the primary circuit. Given that the specific volume of water vapor under low pressure is very large, it is necessary to obtain a fluid transfer rate through the member 4 (FIGS. 1A and 1B) also large. This can naturally be obtained, at least theoretically, by increasing the dimensions of the device 1, namely the capacities of the tanks, the diameters of the conduits, the volumes of the cylinders, etc. However, this solution quickly becomes impractical, in particular as regards the transfer members, and more particularly the moving parts that are the valves and the pistons. Also, in the preferred embodiment, a large nominal flow rate can be obtained by providing a succession of transfer members (cylinders and pistons), arranged in parallel. A practical example of such an embodiment is illustrated by the

  Figures 3A and 3B, in side and front view, respectively.

  To fix the ideas, it was assumed that the device, now referenced 1 ′, included two rows of four transfer members. The cylinders of each row are marked a to d, and the two rows are marked arbitrarily, d and g, for "right" and "left". The same conventions have been adopted for the other elements of the device 1 ′ which relate to one or the other of the eight transfer members. In addition, the elements common to the previous figures have the same references and they do not

  will be described again only as necessary.

  In the example described, it has been assumed that the hot water, coming from the industrial unit (FIG. 2A: U), was stored in the enclosure 90 of an intermediate tank 9 and injected into the device proper by a system comprising a pump 210 and a valve

check valve 211, and line 21.

  According to a first characteristic of this embodiment, the first tank is divided into two: tanks 2a and 2b, delimiting the enclosures 20a and 20b. More precisely, in the illustrated configuration, the tank 2a is arranged vertically and it plays the role of the tank 2 of the device described above. Line 21 enters the enclosure and it includes a spray nozzle 22,

as before also.

  Part of the hot water injected turns into vapor phase, 23 ', while the rest of the water, 23, which is cooled, fills the bottom of the enclosure 20a of the tank 2a, to be rejected or recycled by the usual circuit: line 26, pump 60 and non-return valve 61. Depending on the applications, provision is made or not for additional cold water by

driving 27.

  The tank 2b is in the form of a horizontal cylinder opening into the enclosure 20a. The enclosure 20b of the tank 2b can have the same diameter as that of the enclosure 20a of the tank 2a. In the same way, the tank 3 is advantageously arranged horizontally, parallel to the tank 2b. In reality, the tank 2b constitutes an extension of the tank 2a, which allows easier coupling of the "primary" and "secondary" tanks, taking into account the structure

  particular of fluid transfer members.

  Indeed, on either side of these two parallel tanks, 2b and 3, there are two rows of transfer members, with their associated pipes. Thus, in FIG. 3A, which shows the "straight" part of the device 1 ′, four transfer elements have been shown, referenced 4ad to 4dd. FIG. 3B, in front view, shows the two extreme transfer members, belonging to the right and left rows, that is to say the 4dd members

and 4dg.

  Each of these transfer members, 4ad to 4dg, is quite similar to the single transfer member in Figures 1A and 2A. Only the configuration of the supply and extraction pipes is adapted to the particular arrangement in the space of the tanks 2b and 3, on the one hand, and to the location of the transfer members, 4ad to 4dg, with respect to these tanks, on the other hand. FIG. 3B illustrates the pipes associated with the transfer members 4dd and 4dg, namely the pipes 24dd and 25dd making the enclosure 20b communicate with the cylinder of the transfer member 4dd, the pipes 31dd and 32dd making the enclosure 30 communicate with the cylinder of this same transfer member 4dd, the lines 24dg and 25dg making the enclosure 20b communicate with the cylinder of the transfer member 4dg, and the pipes 31dg and 32dg making the enclosure 30 communicate with the cylinder of this same organ

4dg transfer.

  We find an identical organization for

  other stages (for example figure 3A: 4ad to 4cd).

  As before, these transfer members, 4ad to 4dg, comprise a cylinder and a double-acting piston, as well as two pairs of intake and exhaust valves, one pair for the upper chamber and the other for the lower chamber. In order not to overload the drawing, these elements have not been referenced individually. The pistons are driven by a four-stage machinery (in reality twice four stages), 5ad to 5dg, comprising "rod-crank" systems (not explicitly referenced) and flywheels, 53ad to 53dg. A single motor 8 drives the assembly, for example and in a conventional manner per se, by means of belts, alternately arranged to the right and to the left of the 1 "device: belts on the right 55 and 57, and on the left 56 and 58. The flywheels, 53ad to 53dg, are arranged in pairs on common shafts, 500a to 500d. These shafts rotate in pairs of bearings, right and left, 53ad to 53dg. The bearings, 53ad to 53dg, and the motor 8 are fixed to a lower support Sup of the device 1 ", which can itself be fixed to the ground by

  any appropriate means (not shown).

  To obtain balanced operation of the 1 "device, in particular to avoid vibrations and jolts, it is advantageous to temporally shift the positions of the pistons in the cylinders, in pairs, on the one hand, and in stages by the same row, on the other hand, like

suggests in Figures 3A and 3B.

  The overall operation of the device 1 ", according to the embodiment which has just been described, is quite similar to that of the device 1, as explained with reference to FIGS. 1A to 1B, and it is unnecessary to redescribe it in detail. The essential advantage of the configuration of the 1 "device, due to the parallel connection of several transfer members, is to be able to process a greater useful fluid flow, without being obliged to inconsiderately increase the dimensions of the constituent elements, at least those of the transfer members, 4ad to 4dg, of the piping, and of the

  parts of the machinery, 5ad to 5dg, actuating the pistons.

  For some applications, it is necessary to have steam under high pressure. While retaining the basic architecture of the device in FIGS. 2A and 2B,

  it is possible to obtain such a result.

  To do this, according to an additional embodiment, the device is partitioned into two cascade stages, and more particularly the "secondary" tank.

receiving steam under pressure.

  FIG. 4 illustrates, in side view, such an embodiment. The elements common to the previous figures have the same references and will only be described again

as needed.

  The device, now referenced 1 ", includes two

  parts, or cascade compression stages: eI and eII.

  The stage eI comprises all the elements of the device 1 ′, except that, in the example illustrated in FIG. 4, only three stages of transfer members have been provided per row, for example the organs 4ad to 4cd, for the right part. With this exception, the operation of this stage eI is strictly identical to

  that of the device 1 'in FIGS. 2A and 2B.

  According to another characteristic of this embodiment, the tank of the "secondary" circuit is also

  divided into two tanks, referenced 3a and 3b.

  The vaporized water 23 ′ is transferred into the enclosure 20b of the tank 2b towards the enclosure 30a of this tank 3a, under a higher pressure than that prevailing

in enclosure 20a.

  According to yet another characteristic of this mode of

  realization, the last stage of transfer organs,

  that is to say the pair of right and left organs, of which only the right organ 4'd is visible in FIG. 4, has a particular role. It connects the enclosure 30a of the tank 3a with the enclosure 30b of the tank 3b. The transfer of steam 23 "a takes place again with an increase in the compression ratio (steam 23" b). Also, the upper and lower chambers (not shown) of the cylinders of the pair of transfer members of the last stage eII, communicate with the enclosure 30a via two pipes, 24'd and 25'd, respectively. Similarly, these upper and lower chambers communicate with the enclosure 30b via two pipes, 31'd and 32'd,

respectively.

  The driving machinery is strictly

  identical to that described with reference to FIGS. 3A and 3B.

  It is also possible to generalize the operation of the device 1 ", by adding one or more additional over-compression stages to it, that is to say by providing three or more" secondary "tanks, and not two as illustrated in the figure. 4. There is between each tank a transfer member or a pair of transfer members. On each stage, the vapor pressure obtained

  increases, as does its temperature.

  Given that the vapor, even after a single transfer, is under a pressure much higher than that prevailing in the enclosures of the "primary" circuit, for example in enclosure 23b, it is generally unnecessary to provide several stages of organs because the specific volume of the vapor has greatly decreased. Depending on the steam flow to be obtained, a single transfer device

  may also be sufficient, instead of a pair.

  On reading the above, we can easily see

  that the invention does achieve the goals it has set for itself.

  It should be clear, however, that the invention is not limited to only examples of embodiments explicitly

  described, in particular in relation to FIGS. 1A to 4.

  In particular, the numerical values have been specified only to fix ideas. They depend

  essentially of the precise application targeted.

  Similarly, when there are several, the number of transfer members is not limited to two pairs of four members in parallel. This number essentially depends on the instantaneous quantity of fluid to be treated. Although the configuration in pairs is advantageous, we can also adopt another

  configuration, for example online.

  It must also be clear that, although particularly suitable for cooling and recycling applications of hot or lukewarm water, coming from industrial installations (nuclear power station, etc.), the invention cannot be confined to this single type. of applications. The invention finds application each time it is a question of cooling a fluid in liquid form and of recovering the stored calories, with recycling or not of this fluid, and possible use of the steam generated in accordance with the process, in a form more or less compressed, depending on the type of device used. By way of non-exhaustive examples, mention may be made of cooling milk, various fruit juices, chemical solutions, cooling water from a hot source with a view to producing steam, etc. Finally, although particularly suitable for installations of large powers, the method of the invention is entirely compatible with installations of medium or small powers, or even with

  domestic installations and / or appliances.

Claims (12)

  1. A method of cooling a vaporizable utility fluid with recovery of thermal energy, characterized in that it comprises at least the following repetitive steps: - introduction of said fluid (21) into a first enclosure (20) and vaporization (22 ) under vacuum of a fraction of this fluid (23 '), so as to obtain the cooling of the fraction of non-vaporized fluid (23) and its recovery in the liquid phase; - evacuation (26) of said first enclosure (20) of said fluid in the cooled liquid phase; - Transfer of said fraction of vaporized fluid (23 ') to a second enclosure (30), by means of mechanical coupling means (4) sucking the vaporized fluid (23') out of the first enclosure and discharging it, gas phase (23 ") with a determined compression ratio, in said second enclosure (30); - and evacuation (33) from this second enclosure (30) of said fluid compressed in gaseous phase (23"), so   to obtain said recovery of thermal energy.   2. Method according to claim 1, characterized in that said vaporizable utility fluid comes from an industrial unit (U) in which it has undergone a   determined value warming.   3. Method according to claim 2, characterized in that said fluid cooled in the liquid phase (23) is returned, by a so-called cold fluid circuit (26, 6), in said industrial unit (U) and reintroduced into said first enclosure (20) after reheating 4. Method according to claim 3, characterized in that it comprises an additional step consisting in bringing an additional quantity of said vaporizable utility fluid into said cold fluid circuit, of mass equal to said fraction of vaporized fluid transferred from said first enclosure into said second enclosure,   so as to compensate for this quantity of fluid transferred.   5. Method according to any one of   claims 2 to 4, characterized in that said unit   industrial (U) comprising a generator (Ch) of fluid in gaseous phase, under determined pressure and temperature, and means (Cl-Cn) of heat exchange between this vapor and a circuit (21-26) in which said fluid circulates utility to be cooled, said compressed gas phase fluid (23 ") present in said second enclosure (30) is returned (33) to the industrial unit (U) and said exchange means (C1-Cn), for be recycled there.   6. Method according to any one of   Claims 1 to 5, characterized in that it comprises at   at least one additional step consisting in transferring said compressed gas-phase fluid (23 ") from said second enclosure (30a) to an additional enclosure (30b), by means of additional mechanical coupling means (4'd) sucking the fluid compressed in gas phase (23 "a) out of the second enclosure (30a) and driving it, with an additional compression ratio, into said enclosure additional (30b).   7. Method according to any one of   claims, characterized in that said fluid   vaporizable utility is water.   8. Installation for implementing the process   according to any one of the claims, characterized in   what it comprises at least: - a first enclosure (20) provided, in an upper zone, with a supply pipe (21) of said utility fluid to be cooled, vaporization means (22) of the fluid, connected to said supply line (21), and, in a lower region, a discharge line (26) of said liquid-cooled fluid (23); - a second enclosure (30), provided with a discharge pipe (33) of said fluid compressed in the gas phase (23 "); - and means of transfer (4) of said fraction of vaporized fluid (23 '), mechanically coupling said first (20) and second (30) enclosures, these transfer means (4) comprising a member (40-41) for sucking up this fraction of vaporized fluid (23 ′), outside the first enclosure (20 ), and of discharge, under said determined compression ratio, towards the second enclosure (30), and conduits (24-25, 31-32) opening into the first (20) and second (30)   enclosures, so as to allow said transfer.   9. Installation according to claim 8, characterized in that said first enclosure is double and consists of a vertical enclosure (20a), provided with said supply lines (21) of said utility fluid to be cooled and discharge (26) of said fluid cooled in liquid phase (23), and a horizontal enclosure (20b), opening at one of its ends in said vertical enclosure (20a), in that said second enclosure (30) containing said compressed fluid in gaseous phase ( 23 ") is also horizontal, and in that there is a plurality of transfer means (4ad-4dg) coupling   said horizontal enclosures (20b, 30).   10. Installation according to claim 8 or 9, characterized in that each of said transfer means (4) comprises at least one cylinder (40) provided with a double-acting piston (41), performing back and forth movements. inside said cylinder (40), said piston (41) defining inside said cylinder (40) an upper chamber (400) and a lower chamber (401), in that said upper chambers (400) and lower (401) each communicate said first (20) and second (30) enclosures, via a pair of conduits (24-25, 31-32) opening into these enclosures (20, 30), and that these chambers (400, 401) are provided with intake valves (42,44) on said pipes (24, 25) opening into the first enclosure (20) and exhaust valves (43, 45) on said pipes conduits (31-32) opening into the second enclosure (30), so as to allow said transfer of vaporized fluid (23 '), from the first enclosure (20) to the d second enclosure (30), with said determined compression ratio. 11. Installation according to claim 10, characterized in that each of said double-acting pistons (41) is moved by a rod-crank system   (51-52) driven by a variable speed motor (8).   12. Installation according to any one of   Claims 8 to 11, characterized in that, said   second enclosure (30a) being closed, it comprises at least one additional enclosure (30b) and additional transfer means (4'd) mechanically coupling the second enclosure (30a) to said additional enclosure (30b), so as to transfer said fluid compressed in gas phase (23 "a) from the second enclosure (30a) to said additional enclosure (30b), under a higher compression ratio. Is