WO1999041552A1 - Procede et dispositif de refroidissement d'air - Google Patents

Procede et dispositif de refroidissement d'air Download PDF

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Publication number
WO1999041552A1
WO1999041552A1 PCT/BE1998/000121 BE9800121W WO9941552A1 WO 1999041552 A1 WO1999041552 A1 WO 1999041552A1 BE 9800121 W BE9800121 W BE 9800121W WO 9941552 A1 WO9941552 A1 WO 9941552A1
Authority
WO
WIPO (PCT)
Prior art keywords
canalization
heat exchanger
plates
air stream
fluid
Prior art date
Application number
PCT/BE1998/000121
Other languages
English (en)
Dutch (nl)
Inventor
Antonius Van Hecke
Ernest Berben
Original Assignee
Antonius Van Hecke
Ernest Berben
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from EP98200447A external-priority patent/EP0859203A3/fr
Application filed by Antonius Van Hecke, Ernest Berben filed Critical Antonius Van Hecke
Priority to AU87951/98A priority Critical patent/AU8795198A/en
Publication of WO1999041552A1 publication Critical patent/WO1999041552A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D5/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation
    • F28D5/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, using the cooling effect of natural or forced evaporation in which the evaporating medium flows in a continuous film or trickles freely over the conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0025—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being formed by zig-zag bend plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0081—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by a single plate-like element ; the conduits for one heat-exchange medium being integrated in one single plate-like element

Definitions

  • the present invention concerns a method and device for cooling air.
  • the invention aims a method and device with which these disadvantages are excluded, in other words with which air can be cooled very efficiently in a relatively inexpensive manner with little energy consumption. It is meant in particular for applications in which the use of compression cooling devices is not economically feasible, but in fact it can be used for any application whatsoever.
  • the invention concerns a method for cooling air, characterized in that it consists in the cooling of an air stream on the one hand by sending it through a primary canalization of a heat exchanger, and by vaporizing fluid, in particular water, in a secondary canalization of this heat exchanger on the other hand by means of an auxiliary air stream which is tapped off the air stream leaving the primary canalization.
  • the fluid to be evaporated is hereby sprayed or atomized on the walls of the secondary canalization or provided on it in any other way whatsoever.
  • a heat exchanger with plates This offers the advantage that very large evaporation surfaces are created, so that the auxiliary air stream can be limited to a minimum and so that there is little loss of energy.
  • the use of a heat exchanger with plates also offers the advantage that large surfaces can be easily moistened by means of one and the same spray device .
  • the moisture is sprayed on the plates, atomized respectively, with drops having a size in the order of 100 to 300 micrometre, which produces the best evaporation effect.
  • the auxiliary air stream is cooled and/or dried before it can be guided through the secondary canalization.
  • the air of the auxiliary air stream can absorb more moisture, which promotes the evaporation of the fluid.
  • care will be taken, in any way whatsoever, that the air of the auxiliary air stream is supplied to the heat exchanger with a relative air humidity which is lower than 80%.
  • the auxiliary air stream in the secondary canalization will be preferably guided in the upward direction through the heat exchanger.
  • the auxiliary air stream is not counteracted by the chimney effect of the hot, damp air which occurs in the secondary canalization, so that the auxiliary air stream is made more efficient.
  • measures are taken which make sure that the air of the auxiliary air stream is evenly distributed through the secondary canalization of the heat exchanger.
  • these measures make sure that no parts are created in the secondary canalization in which the air stands practically still.
  • the air supply and/or the air extraction according to the invention will preferably be realized in a direction which extends diagonally or almost diagonally on the plates of the heat exchanger in order to make sure that the auxiliary air stream flows evenly distributed through the secondary canalization.
  • an obstruction is provided on the inlet of the secondary canalization, which is provided with passages in the shape of perforations, holes or such.
  • the walls of the secondary canalization are provided with means which retain the fluid on the one hand, but which also distribute it over the surface concerned on the other hand.
  • these are means which provide for a hygroscopic surface.
  • these means will consist of a hygroscopic coating, preferably in the shape of a hygroscopic membrane, cloth or such.
  • the use of such means offers the advantage that the moisture is optimally distributed over the surface and is retained on the surface .
  • This in turn offers the advantage that the walls of the secondary canalization will be moistened with great certainty over their entire surface, so that an evaporation and cooling takes place over the entire surface.
  • This also offers the advantage that fluctuations in the supply of moisture do not immediately result in excess fluid running out of the canalization, so that a receptacle can possibly be omitted.
  • the fluid to be evaporated will preferably be supplied in the secondary canalization counterflow in relation to the auxiliary air stream. This optimally prevents moisture pollution in the dry parts of the device. Moreover, all the supplied fluid will be evaporated with, great certainty, and it is practically excluded that an excess of non-evaporated fluid is 5 created on the inlet of the secondary canalization.
  • canalizations are used both for the main air stream and for the auxiliary air stream which do not have any open receptacles and/or leak-off ladles.
  • all the supplied fluid will preferably be evaporated according to the invention, so that collecting means such as a receptacle or leak-off ladle are no longer necessary.
  • the invention also concerns a device for cooling air which makes it possible to realize the above-mentioned method.
  • This invention consists of a heat exchanger having a primary canalization and a secondary canalization; means which put fluid on the walls of the secondary canalization so as to create a cooling effect due to evaporation; pipes which provide for a main circuit through the primary canalization and an auxiliary circuit through the secondary canalization, whereby the auxiliary circuit forms a branch on the main circuit, downstream of the primary canalization; and means to create the above-mentioned air stream and auxiliary air stream.
  • figure 1 schematically represents a device according to the invention
  • figure 2 shows the heat exchanger of the device from figure 1 in perspective, also in a schematic way
  • figure 3 illustrates the variation in temperature and humidity in a diagram for the device of figure
  • figure 4 schematically represents a variant of the device in figure 1; figure 5 illustrates the variation in temperature and humidity in a diagram for the device of figure
  • figure 6 schematically represents yet another variant of the device in figure 1; figure 7 illustrates the variation in temperature and humidity in a diagram for the device of figure
  • figure 8 shows a variant of the heat exchanger in figure 2; figure 9 shows a schematic section according to line
  • figure 8 shows a section according to line X-X in figure 9 to a larger scale, for another embodiment; figures 11 and 12 show views according to arrows Fll and F12 in figure 10 to a smaller scale; figure 13 schematically represents a variant of the device according to the inven ion; figure 14 schematically represents a section according to line XIV-XIV in figure 13; figure 15 shows a section according to line XV-XV in figure 14 to a smaller scale; figure 16 schematically represents another device; figure 17 shows a practical embodiment of the part which is indicated with F17 in figure 14 to a larger scale; figure 18 schematically represents another device according to the invention; figure 19 shows a practical variant of the part which is indicated in figure 17; figure 20 shows the part which is indicated with F20 in figure 19 to a larger scale.
  • figure 21 shows a particularly practical embodiment of the part which is represented in figure 17; figure 22 shows a section according to line XXII- XXII in figure 21 to a larger scale.
  • the device 1 mainly consists of a heat exchanger 2 , in this case a heat exchanger with plates with a primary canalization 3 and a secondary canalization 4; spray means 5 which can put finely divided fluid 6 on the walls of the secondary canalization 4 so as to create a cooling effect due to evaporation; pipes which are not represented, providing in a main circuit 7 through the primary canalization 3 and in an auxiliary circuit 8 through the secondary canalization 4, whereby the auxiliary circuit 8 forms a branch on the main circuit 7, whose branching point 9 is situated downstream of the primary canalization 3; and means 10 to create an air stream 11 through the primary canalization 3 and an auxiliary air stream 12 through the secondary canalization 4.
  • a heat exchanger 2 in this case a heat exchanger with plates with a primary canalization 3 and a secondary canalization 4
  • spray means 5 which can put finely divided fluid 6 on the walls of the secondary canalization 4 so as to create a cooling effect due to evaporation
  • pipes which are not represented, providing in a main circuit 7 through the primary
  • the heat exchanger 2 consists of a number of plates 13-14 situated next to one another, in between which rooms 15- 16 are provided which alternately form passages for the 8 air stream 11 and the auxiliary air stream 12.
  • the inlets, outlets respectively of these rooms 15-16 are situated such that, as represented in the figures, the air stream 11 and the auxiliary air stream 12 intersect one another in the heat exchanger 2.
  • the means 10 to create the air stream 11 and the auxiliary air stream 12 consist of one common fan 17 in the example represented, but it is clear that several fans or such can be incorporated in the main circuit 7 and/or the auxiliary circuit 8.
  • the heat exchanger 2 is erected such in this example that the secondary canalization 4 extends from top to bottom. Under the heat exchanger 2 is erected a receptacle 18 to collect any moisture dripping down.
  • the above-mentioned spray means 5 in this case consists of a sprinkler 19 which is fed by means of a pump 20 or such, tapping fluid 6, in particular water, from the receptacle 18.
  • the level of the fluid 6 in the receptacle 18 is maintained thanks to a connection to a supply net 21, preferably a mains system for water.
  • the level in the receptacle 18 can hereby be adjusted by means of a valve 22 which is controlled by a float 23.
  • the sprinkler 19 which in reality may have several sprinkler heads, is situated above the set of plates 13- 14 and is made such that the fluid 6 concerned is sprayed over the entire surface of the plates 13-14.
  • the working of the device 1, as well as the accompanying method, consists in that an air stream 11 is sent through the primary canalization 3 by the means 10. This air stream 11 is split in a main air stream 24 and an auxiliary air stream 12. The auxiliary air stream 12 makes sure that the fluid 6 sprayed on the plates 13-14 by means of the spray means 5 evaporates .
  • the different situations A, B and C which are represented in the diagram of figure 3, are situations which may occur in the places which are correspondingly indicated by A, B and C in figure 1.
  • a cooling temperature is created on the plates 13-14 which is almost equal to the wet point temperature in point C of the diagram.
  • Figure 4 represents a variant in which a cooler 25 and a heat source 26, together forming a drier and which are either or not combined in one appliance, are incorporated between the above-mentioned branch point 9 and the secondary canalization 4 of the heat exchanger 2.
  • This is preferably a conventional cooler 25 providing for a compression cooling.
  • the heat source is preferably adjusted such that the relative humidity of the auxiliary air stream remains below 80% behind the drier.
  • Figure 6 represents a variant of the device 1 whereby use is made of a drier 27 in the auxiliary circuit 8 provided with a drying agent which can be regenerated, for example silica gel.
  • the air coming from this drier 27 will normally be cooled before it is used for the evaporation of the fluid 6 in the secondary canalization 4.
  • the heat exchanger 2 is provided in an auxiliary canalization 28 for the cooling of the auxiliary air stream 12.
  • auxiliary canalization 28 which consists of a heat exchanger provided in the main air stream behind the branching point 9.
  • Figure 8 schematically represents a variant whereby the plates 13-14 are erected key-shaped, such that the secondary canalization 4 narrows according to the direction of flow.
  • the fluid 6 sprayed between the plates 13-14 can efficiently cover the entire surface of these plates 13-14, even when the sprinkler 19 is situated above these plates 13-14.
  • the device 1 is also equipped with an element 29 such as a perforated plate to distribute the air evenly over the different rooms 16 of the secondary canalization 4, so that the air is optimally used for the evaporation and so that the flow rate of the auxiliary air stream 12 can be limited to a minimum.
  • an element 29 such as a perforated plate to distribute the air evenly over the different rooms 16 of the secondary canalization 4, so that the air is optimally used for the evaporation and so that the flow rate of the auxiliary air stream 12 can be limited to a minimum.
  • Figure 9 further illustrates how the whole can be provided with pipes or ducts 30, 31 and 32 to guide the supplied air stream 11, the auxiliary air stream 12 and the main air stream 24.
  • the main air stream 24 hereby forms the useful part of cooled air.
  • Figure 10 shows a section of yet another part of a practical embodiment, whereby guiding means 33 in the shape of ribs 34-35-36-37 are provided in the primary canalization 3 which force the air of the air stream 11 to the narrowest part 38 of the rooms 15 so as to obtain an optimal heat transmission.
  • the ribs 34-35 are hereby provided on the plates 13.
  • the ribs 36-37 are provided on the plates 14 and end up between the ribs 34-35 when the whole is mounted, as indicated in figures 11 and 12. 12
  • guiding means are also provided in the secondary canalization 4 which promote the intersected circulation and which consist of ribs 39-40 in this case.
  • the ribs 34-35-36-37-39-40 also form reinforcements for the plates 13-14.
  • the plates 13-14 are preferably clasped together with their edges in this case.
  • a large number of difficult connections is excluded.
  • the key-shaped rooms 15-16 preferably have an opening of about 2.5 mm wide on their narrowest side and an opening of about 7.5 mm wide on their widest side.
  • the auxiliary air stream 12 can be guided from top to bottom through the heat exchanger 2 and good results can be obtained, the inventor found that these results can even be significantly improved by guiding the auxiliary air stream 12, according to a preferred characteristic of the invention, in the upward direction through the heat exchanger, either vertically, as represented in figures 13 to 15, or upward in a diagonal direction.
  • the chimney effect is meant the natural phenomenon that hot air has a tendency to rise by itself.
  • a lead- through of the auxiliary air stream 12 according to the 13 directions which are represented in this figure, may have for a result that certain wall parts 41, which are schematically represented in figure 16 by means of a hatching, participate little in the evaporation process, as the flow rate of the air stream moving alongside of them is too low, due to the fact that the auxiliary air stream 12 tries to find the easiest way.
  • this can be remedied by making sure that the air of the auxiliary air stream flows evenly distributed through the secondary canalization 4 of the heat exchanger 2.
  • use can be made to this end of an element 29 which is provided on the inlet of the secondary canalization 4, which forms an obstruction and is provided with perforations or such.
  • the use of such an element 29 or any other obstructive element can be excluded while an even distribution is nevertheless obtained by having the air supply 42 and/or air extraction 43 take place right before and right behind the plates 13-14 according to a direction which extends diagonally or almost diagonally on the plates 13- 14, with the help of suitable ducts 44 and 45, as represented in figures 13 to 15.
  • the creation of wall parts 41 alongside which the flow of air is practically zero is excluded. 14
  • the walls 46 of the secondary canalization 4 are provided with a hygroscopic coating 47, in this case a membrane which is provided against the walls 46, for example stretched around it.
  • This coating 47 directly and indirectly offers several advantages, including the following:
  • the application and distribution of the fluid 6 over the entire surface of the walls 46 is no longer critical . Thanks to the hygroscopic effect of the coating 47, the fluid will spread automatically once it has ended up on the coating 47.
  • the fluid 6 no longer necessarily has to be sprayed and/or atomized in a finely distributed manner. It is sufficient that more or less an equal amount of fluid ends up on each of the plates 3-14.
  • the sprinklers 19 no longer have to be erected such that the walls 46 are situated entirely within their field of vision.
  • the hygroscopic coating 47 makes sure that the fluid 6 is distributed over the entire surface of the walls 46, even over the parts of these walls 46 which are situated outside the field of vision of the sprinklers 19.
  • the plates 13-14 of the above-mentioned heat exchangers 2 will preferably be erected upright, and the air stream 11 will be mainly guided in the horizontal direction through the 15 heat exchanger 2, whereas the auxiliary air stream 12 will be mainly guided through it in the vertical direction, whereas the air supply 42, the air extraction 43 respectively, of the auxiliary air stream 12 on the plates 13-14 takes place laterally, as is clearly shown in figure 14.
  • the fluid 6 to be evaporated is supplied counterflow as of the outlet of the secondary canalization 4, which, as explained in the introduction, offers several extra advantages.
  • the sprinkler 19 can hereby make a rotating movement F to and fro.
  • the figures 13 to 15 and 18 also show that a heat exchanger 2 can be used according to the invention which does not have a receptacle, as opposed to for example the embodiment of figure 1, in which such a receptacle 18 is used. This offers the advantage that the air no longer has to be guided over a liquid mass and consequently cannot arbitrarily absorb any moisture.
  • the amount of supplied fluid 6 must be dosed such in this case that it can evaporate entirely, in other words such that there is no dripping moisture . 16
  • this is realized by adjusting the supply of the fluid 6 by means of a controlled regulating valve 51.
  • the regulating valve 51 can be controlled by means of a control unit 51A and/or a sensor which supplies measured values which are directly or indirectly representative for the moistening degree in the secondary canalization or by means of any feedback whatsoever.
  • the heat exchanger 2 is preferably built up of longitudinal plates 13-14 according to a preferred embodiment.
  • the distance Dl between the plates of the secondary canalization 4 will be smaller than 5 mm. This relatively small distance offers as an advantage that no excess air, which produces no evaporation effect, will flow through the secondary canalization.
  • the heat exchanger 2 will have a flow-through length LI between the plates in the primary canalization 3 of 40 to 80 cm.
  • the number of plates 13-14 can be selected as a function of the flow rate to be treated. In practical embodiments, this number will be several times ten and even 100 to 200.
  • the plates 13-14 themselves can be made of a thin and good heat-conducting material, for example a thin metal plate. However, it was found that also other materials provided good results on condition that the plates 13-14 are maintained relatively thin. According to the invention, the plates 13-14 will preferably even be made of synthetic material, which offers the advantage that a heat exchanger 2 is obtained which is highly corrosion- resistant and which can be realized in a relatively inexpensive manner.
  • the plates 13-14 will be made of polycarbonate plate or polypropylene plate, for example with a thickness D2 of 0.3 mm.
  • Figures 19 and 20 represent a practical embodiment in which the above-mentioned plates 13-14 are made continuously of a single corrugated plate 53, whereby the spaces 15-16 provided alternately in between are used for the formation of the primary canalization 3, the secondary canalization 4 respectively.
  • a sealing wall 54 is provided on one side against said corrugated plate 53.
  • passages 55 are provided which connect the space under this sealing element 54 to the above-mentioned spaces 16.
  • corrugated plate 53 offers the advantage that the whole can be realized in a relatively simple manner, as no separate plate structure has to be build up.
  • corrugated plate 53 will preferably be formed starting from a flat plate, which plate will subsequently be heated, and by deforming this heated plate by sucking it in over a comb-shaped mould.
  • auxiliary air stream 12 is also formed in this case near the inlet, as the air has to flow locally through the passages 55. This results in a slight pressure increase in the space under the sealing wall 54, so that the air is forced to spread entirely over this space and to flow through all the passages 55.
  • a forced extraction will preferably be provided for, by means of for example a fan 56, which is only represented as an example in figure 18.
  • the means for supplying the fluid 6 do not necessarily have to be spray means. Especially in the case where use is made of an absorbent or hygroscopic coating 47, a fine atomization is not necessary and one could for example also use a drip system or such.
  • an auxiliary air stream 12 will preferably also be provided with such a flow rate that the refreshment of the air in the secondary canalization 4 takes one to three volume units per second, whereby by a volume unit is meant the volume of air available in the secondary canalization 4, in particular between the plates 13-14 or other heat transfer elements of the heat exchanger 2.
  • Figures 21 and 22 represent yet another embodiment in which use is made of a package 57 of hollow, plate-shaped elements 58 for forming the canalizations 3 and 4, in particular extruded plastic plates, whereby the passages 59 in these elements 58 form the primary canalization 3 and the passages 60 between the different elements 58 form the secondary canalization 4.
  • the coating 47 consists of a cloth, membrane or such 20 which is stretched around the above-mentioned elements 58.
  • a practical method for fixing this coating 47 consists in that it is wound around the elements 58 and fixed by means of one or several thermal joints 61.
  • FIG. 21 and 22 also makes clear that the fluid supply no longer necessarily has to be carried out by means of sprinklers, but that it can also be obtained by supplying fluid directly up to the coating 47, i.e. without atomizing the fluid.
  • this is realized by means of a pipe system with fluid supply pipes 62 which communicate with the coating 47 by means of openings 63, through which the fluid is slowly supplied.
  • the distribution of the fluid can possibly be further improved by providing distributing elements 63 made of a fluid-absorbing and/or hygroscopic material and extending in the longitudinal direction at the height of the elements 58, in particular on their top sides, which communicate with the hygroscopic surface over their entire or almost entire length, i.e. in this case with the coating 47.
  • These distributing elements 63 consist of rope, tent, or such. According to a variant which is not represented here, they might also consist of a thickening in the absorbing and/or hygroscopic material provided on the wall of the secondary canalization 4, extending in the longitudinal direction.
  • These distributing elements 63 are provided in seatings 64 in the top edges of the elements 58 and they are kept in place as the coating 47 is stretched around them. 21
  • Figures 20 and 21 further show that, if necessary, a similar collecting system 65 can be provided at the bottom to collect the excess water in discharge pipes 67 via absorbing elements 66.
  • figure 21 only represents a part of the device and that, in practice, the required partition walls will be provided so as to keep the primary and secondary canalization in the heat exchanger separated.
  • the distributing elements 63 may also consist of an absorbing filler, a cloth rolled up so as to form a rope or such.
  • the hygroscopic wall can also be realized in other ways than with a coating 47, for example by making the walls directly out of an absorbing and/or hygroscopic, for example porous material, whereby an impermeable sealing is preferably provided on the side of the primary canalization 3 in this case. According to a variant, this sealing can be omitted on condition that the evaporation is constantly so large that no liquid penetrates into the primary canalization 3.
  • the air tapped off from the main stream will be dried by means of a drying agent that can be regenerated which will release the absorbed moisture when an electric tension is supplied to it, in particular a drying agent on the basis of zeolite.
  • a drying agent on the basis of zeolite.
  • Use can hereby be made of a zeolite adsorbent in the shape of granules which are for example immobilized between two grids, such that the air can go through it and the granules can absorb the moisture contained in it .
  • the drying agent for example to the two grids, the moisture will be released by the granules in a relatively short time, i.e. in just a few minutes. The discharging of the adsorbed moisture in said short time barely has any influence on the good working order of the air cooling system.
  • the invention also concerns embodiments whereby only a part of the auxiliary air stream is supplied via the branch, and whereby the other part is for example drawn from the environment via a separate suction.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un procédé de refroidissement d'air, caractérisé en ce qu'il consiste à refroidir un écoulement d'air (11) d'une part en l'envoyant à travers une première canalisation (3) d'un échangeur thermique (2) et en vaporisant, d'autre part, du fluide (6), plus particulièrement de l'eau, dans une seconde canalisation (4) de cet échangeur thermique (2) au moyen d'un écoulement d'air auxiliaire (12) qui est prélevé à partir de l'écoulement d'air (11) quittant la première canalisation (3).
PCT/BE1998/000121 1998-02-13 1998-08-06 Procede et dispositif de refroidissement d'air WO1999041552A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU87951/98A AU8795198A (en) 1998-02-13 1998-08-06 Method and device for cooling air

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP98200447A EP0859203A3 (fr) 1997-02-13 1998-02-13 Procédé et dispositif pour refroidissement d'air
EP98200447.5 1998-02-13

Publications (1)

Publication Number Publication Date
WO1999041552A1 true WO1999041552A1 (fr) 1999-08-19

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PCT/BE1998/000121 WO1999041552A1 (fr) 1998-02-13 1998-08-06 Procede et dispositif de refroidissement d'air

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AU (1) AU8795198A (fr)
WO (1) WO1999041552A1 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003091632A1 (fr) * 2002-04-26 2003-11-06 Oxycell Holding B.V. Refroidisseur a condensation sous la forme d'une structure ou d'une partie de celle-ci
NL1023471C2 (nl) * 2003-01-23 2004-07-26 Oxycell Holding Bv Dauwpuntskoeler met antimicrobiele voorzieningen.
NL1022799C2 (nl) * 2003-02-27 2004-08-30 Oxycell Holding Bv Dauwpuntskoeler met losneembare irrigatiemiddelen.
NL1026096C2 (nl) * 2004-05-03 2005-11-07 Statiqcooling B V Enthalpie-uitwisselaar en werkwijze voor het uitwisselen van enthalpie tussen twee media middels een dergelijke enthalpie-uitwisselaar.
US7181918B2 (en) 2004-03-25 2007-02-27 Oxycell Holding B.V. Vehicle cooler
WO2007061298A1 (fr) * 2005-11-28 2007-05-31 Optimair Holding B.V. I.O. Dispositif de refroidissement a la temperature de rosee
US7415837B2 (en) 2002-04-26 2008-08-26 Oxycom Beheer B.V. Dewpoint cooler
EP2362933A1 (fr) * 2008-11-13 2011-09-07 F.F. Seeley Nominees Pty Ltd Construction de refroidisseur évaporatif indirect
JP2021018013A (ja) * 2019-07-18 2021-02-15 ブラザー工業株式会社 空調機

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FR2238121A1 (fr) * 1973-07-18 1975-02-14 Munters Ab Carl
US4660390A (en) * 1986-03-25 1987-04-28 Worthington Mark N Air conditioner with three stages of indirect regeneration
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WO2003091632A1 (fr) * 2002-04-26 2003-11-06 Oxycell Holding B.V. Refroidisseur a condensation sous la forme d'une structure ou d'une partie de celle-ci
US7861549B2 (en) 2002-04-26 2011-01-04 Oxycom Beheer B.V. Dewpoint cooler
US7415837B2 (en) 2002-04-26 2008-08-26 Oxycom Beheer B.V. Dewpoint cooler
NL1023471C2 (nl) * 2003-01-23 2004-07-26 Oxycell Holding Bv Dauwpuntskoeler met antimicrobiele voorzieningen.
WO2004065857A1 (fr) * 2003-01-23 2004-08-05 Oxycell Holding Bv Refroidisseur evaporatif a dispositions antimicrobiennes
US7428823B2 (en) 2003-01-23 2008-09-30 Oxycell Holding B.V. Evaporative cooler with antimicrobial provisions
EA008655B1 (ru) * 2003-02-27 2007-06-29 Оксицелл Холдинг Бв Испарительный охладитель
WO2004076931A3 (fr) * 2003-02-27 2004-10-28 Oxycell Holding Bv Refroidisseur par evaporation
NL1022799C2 (nl) * 2003-02-27 2004-08-30 Oxycell Holding Bv Dauwpuntskoeler met losneembare irrigatiemiddelen.
JP2006519353A (ja) * 2003-02-27 2006-08-24 オキシセル・ホールディング・ビーブイ 蒸発冷却器
US7775064B2 (en) 2003-02-27 2010-08-17 Oxycom Beheer B.V. Evaporative cooler
US7181918B2 (en) 2004-03-25 2007-02-27 Oxycell Holding B.V. Vehicle cooler
WO2005106343A1 (fr) * 2004-05-03 2005-11-10 Statiqcooling B.V. Echangeur enthalpique et procede permettant l'echange enthalpique entre deux milieux via ledit echangeur enthalpique
NL1026096C2 (nl) * 2004-05-03 2005-11-07 Statiqcooling B V Enthalpie-uitwisselaar en werkwijze voor het uitwisselen van enthalpie tussen twee media middels een dergelijke enthalpie-uitwisselaar.
AU2006317768B2 (en) * 2005-11-28 2010-12-09 Optimair Holding B.V. Dewpoint cooling device
WO2007061298A1 (fr) * 2005-11-28 2007-05-31 Optimair Holding B.V. I.O. Dispositif de refroidissement a la temperature de rosee
US8499576B2 (en) 2005-11-28 2013-08-06 Optimair Bv Io Dewpoint cooling device
EP2362933A1 (fr) * 2008-11-13 2011-09-07 F.F. Seeley Nominees Pty Ltd Construction de refroidisseur évaporatif indirect
EP2362933A4 (fr) * 2008-11-13 2014-03-12 Seeley F F Nominees Construction de refroidisseur évaporatif indirect
US8783054B2 (en) 2008-11-13 2014-07-22 F.F. Seeley Nominees Pty. Ltd. Indirect evaporative cooler construction
JP2021018013A (ja) * 2019-07-18 2021-02-15 ブラザー工業株式会社 空調機
JP7379897B2 (ja) 2019-07-18 2023-11-15 ブラザー工業株式会社 空調機

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