Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
  • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
  • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements
• • 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
  • F24F1/0087—Indoor units, e.g. fan coil units with humidification means
• • 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
  • 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
  • F24F1/0067—Indoor units, e.g. fan coil units characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
• • 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
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F2225/00—Reinforcing means
  • F28F2225/04—Reinforcing means for conduits

Definitions

• the present invention relates to an apparatus for in ⁇ direct evaporative cooling of a useful air current, in ⁇ cluding a contact body made up from layers with ducts therebetween, the ducts being divided into two separate systems, where the useful air passes through the ducts of one system for cooling and where cooling air passes through the ducts of the other system such as to cool the useful air current, cooling being achieved to a sub ⁇ stantial extent by the evaporation of water in the coo ⁇ ling air of the other duct system.
• Apparatus of this kind can be used, e.g. as indirect evaporative heat exchangers for such purposes as cooling of a useful air current in ventilation systems.
• the chief object of the invention is to provide an apparatus of the kind mentioned in the introduction, with a configuration such that good heat transfer and favourable current conditions are afforded in its use as an evaporative heat exchanger, the configuration especially enabling the useful air current to have an horizontal flow direction for the apparatus readily to be incorporated in ventilation plants, where the normal duct system is horizontal.
• Figure 1 is a side view of an embodiment in accordance with the invention.
• Figure 2 is a horizontal section along the line II-II in Figure 1.
• Figure 3 illustrates the flow of the cooling air in the apparatus of Figure 1.
• Figure 4 is a view similar to the one in Figure 3, but with an modified embodiment.
• Figures 5a-5c are cross sections of the layer structure in an inventive apparatus.
• Figure 6 is a side view of a plate or panel of the kind required for making up the structure of the apparatus illustrated in Figure 1.
• Figure 7 is a side view of a heat exchanger unit built in modules.
• the contact body 10 illustrated in Figure 1 is used as an indirect heat exchanger for a useful air current flowing substantially horizontally through the contact body which air is to be cooled and is supplied to the inclined end wall surface 28 illustrated in Figure 1 constituting the inlet to a first duct system in the contact body 10 the useful air current flowing through this duct system in the longitudinal direction of said ducts or gaps, which are separate from adjacent ducts or gaps in a second duct system passed through by a cooling air current.
• the contact body 10 may be made up from a plurality of flat plates 11-15, these being put together with flange-like stiffe ⁇ ning and surface magnifying means therebetween, as illu ⁇ strated in Figure 5, these means being in the embodiment shown corrugated metal sheets or foils 16.
• the corruga ⁇ tions in the sheets 16 constitute the ducts for the useful air which is to be cooled in the contact body 10, the sheets 16 being oriented with their corrugations exten ⁇ ding in the flow direction of the air.
• the corrugated foil or sheet 16 thus defines the width of the ducts or gaps in the contact body through which the useful air passes.
• the corrugations of the sheet 16 must be in good heat conductive contact with the surfaces of the flat plates 11-15. When there are several layers, the crests of the corrugations shall be immediately opposite each other which increases the stability of the body and gives a shorter path for heat conduction.
• the plates 11-15 and corrugated sheets 16 are of a thin material with good heat conductivity, e.g. aluminum and are joined to each other by heating, gluing or other suitable method. They may, for example, be made as intrin ⁇ sically stiff sandwich elements. As will be seen from Figure 5, a desired number of such elements are joined to each other with an intermediate space determined by spacers 32 ( Figure 6) arranged between them. The spacers thus also define the width of the gaps 18 in the second duct system in the contact body, through which the coo ⁇ ling air current shall pass.
• the walls of the gaps 18 are wetted in a manner known per se. Tho surface of the plates or foils 11-15 facing towards the gaps 18 is provided with a coating 20 of a water-absorbing and/or soaking material. During the passage of the cooling air through the gaps 18 there will be evaporation of water into the cooling air, so that an intensive trans ⁇ ference of heat is obtained from the useful- air in the first duct system to the cooling air in the gaps 18, thus reducing the temperature of the useful air to a low value.
• the walls are normally only kept moistened to the extent necessary for evaporation.
• Tha gaps passed through by the cooling air can be made considerably narrower, due to the evaporative cooling effect, than the gaps passed through by the useful air, this being readily enabled by the inventive configuration, where the sandwich elements 12, 14, 16 and the gaps (spacers) 18 can be made to any desired width and mutually indepen ⁇ dently.
• the amount of cooling air is also normally less than that of the useful air, due to the evaporative effect.
• the flanges of the stiffening means or corrugated sheets 16, included in the sandwich element 12-16 consti ⁇ tutes a large heat transfer surface which is brushed over by the passing useful air current.
• the intrin ⁇ sically stiff panels are fabricated from five flat plates or foils 11-15 with intermediate corrugated sheets or foils 16, but they may of course be made up of only two flat plates or foils 11, 15 with one intermediate corruga ⁇ ted sheet or foil 16 (Figure 5a) or three flat plates (foils) and corrugated sheets (foils) 16 (Figure 5b) depending on the desired stiffness and heat transfer surface desired.
• the configuration in several layers has the advantage that the wet gap can be made wider and will less sensitive to variations in the gap width. There will also be fewer panels to handle and they will also be stronger.
• the described apparatus 10 is coupled into a venti ⁇ lation system such that the useful air is drawn in through the ducts formed by the sheets 16 into the first duct system with the aid of a fan 22 ( Figure 1).
• a part of the air current, e.g. 10-50%, of this cooled useful air current is returned as a cooling air current in counterflow to the useful air current through the sec ⁇ ond duct system 18, where the useful air is -moistened by water supplied through jets 24 on the upper part of the apparatus 10, whereat the described, evaporative cooling takes place.
• the cooling air current through the apparatus 10 is provided by a second fan 23, which takes the cooling air to an outlet or to an exhaust air duct.
• the useful air current is passed to the useful air duct in the ventilation system, or directly to a space that is to be air conditioned.
• Figure 2 shows how the major part of the useful air current leaves the ducts 16 as cooled air to flow out into a room or a fresh air duct in a ventilation system, while a partial current is turned to enter the ducts 18 to form the cooling air current, as described above.
• the plates 11- 15 are preferably made rectangular, but at one vertical end, the left one in the Figures, they are given the shape preferably of an unequal sided triangle to form a connection part where the shorter side 26 constitutes the outlet from the second duct system 18, while the longer side 28 constitutes the inlet to the duct system 16.
• a sealing strip 30 is disposed between the plates 11, 15 contiguous to the ducts 18, as illustrated in Figure 6.
• the spacers 32 that determine the width of the ducts 18.
• sealing strip 30 forms a spacer too.
• the more or less dot-shaped spacers 32 can also be replaced by corrugated strips at the upper and lower edges of the sheets 11, 15 as well as the right-hand end thereof. The corrugations in the strips then follow the respective directions of the water or the cooling air current.
• the flow of the cooling air current in a duct 18 is depicted in Figure 3, showing that the cooling air cur ⁇ rent flows from the right side of the body to the outlet 26.
• the other duct system includes ducts 18 extend ⁇ ing over the entire surface of the sheet and which are not divided by intermediate walls or corrugations, it may happen that upwardly the cooling air current has a tendency to deviate upwards where the ducts are open towards the water supply jets 24, such as indicated by the upper dashed line in Figure 3. Different measures may be taken to reduce this deviation tendency, e.g. intermediate walls 34 can be arranged between the jets 24, as seen in Figure 4. It will also be seen from Fi ⁇ gure 3 that the body is provided with a collection trough 36 for excess water. If so desired, recircula- tion of water from the trough to the jets 24 can be arranged.
• intermediate walls 35 can be arran ⁇ ged in the trough 36 to extend down to the normal level of the water in the trough, thus to obstruct downward deviation of the air. In this way the cooling air in the contact body both upwardly and downwardly will flow substantially horizontally in heat exchanging association with the useful air currents in the ducts 16.
• cooling air current is retained within the duct system 18.
• a leakage therefrom due to portions of the cooling air passing by outside the active heat transferring surface has a doubly nega ⁇ tive effect on the cooling.
• the cooling is namely depen ⁇ dent on both amount and temperature of the cooling air. If the amount decreases due to bypassing, the decreased amount of air has a reduced capacity for attracting from the air currents in the ducts 16, which leads to their leaving the ducts 16 at a raised temperature. This raised temperature results in that the cooling air currents also get an increased temperature, which further enfeeb ⁇ les their capacity to attract energy.
• the negative effects on cooling thus combine very deleteriously and with this background it will be understood why it is so important to prevent the mentioned bypassing tendency.
• the triangular inlet part of the duct system 16, which also constitutes the outlet 28 for the ducts 16 is dispo ⁇ sed such that a substantially lower flow resistance is obtained than in the pack itself.
• This may be achieved by the corrugated sheets being replaced here by a sheet with deeper corrugations or by a plurality of strips which stiffen up the inlet part without exercising any substantial resistance to the air flow. Examples of such strips are illustrated at 27 in Figure 1. It will be seen from the Figure that the inlet and outlet parts 26, 28 are unequally sided, i.e. the inlet for the use ⁇ ful air current will be greater than the outlet 26 for the cooling air current. This difference in size can vary and is dependent on the size of the air currents.
• the outlet for the moist cooling air current is also suitably directed upwards to prevent any unnecessary entrainment of water from the moist ducts 18.
• the inlet 28 to the useful air current duct system 16 could comprise the entire vertical side with the cooling air current being taken out vertically upwards.
• the illu ⁇ strated triangular implementation gives other advantages, however, and these are described below.
• a plurality of modules or contact bodies 10 can be built on to each other into a larger unit.
• the useful air can be supp ⁇ lied to the contact bodies 10 via the inlets 28 and the cooling air current taken away from the bodies via the outlets 26 in a very simple way due to the triangular implementation of the inlet/outlet part.
• Another advan ⁇ tage with this implementation is that water can be com ⁇ monly supplied to all the contact bodies 10 at the upper side of the pack via the jets 24 and be collected at the bottom of the pack in the trough 36. The same water thus runs through all the modules 10 via their duct sys ⁇ tems 18.
• the illustrated combination of several contact bodies or modules 10 does not cause any change in the thermodynamics either.

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

Priority Applications (1)

Applications Claiming Priority (2)

Publications (1)

Family

ID=20361124

Family Applications (1)

Country Status (5)

Cited By (4)

Families Citing this family (1)

Citations (2)

• 1985
  • 1985-08-16 SE SE8503854A patent/SE460151B/sv not_active IP Right Cessation
• 1986
  • 1986-08-14 AU AU63334/86A patent/AU6333486A/en not_active Abandoned
  • 1986-08-14 EP EP86905456A patent/EP0269634B1/de not_active Expired - Lifetime
  • 1986-08-14 WO PCT/SE1986/000367 patent/WO1987001188A1/en active IP Right Grant
  • 1986-08-14 DE DE8686905456T patent/DE3676707D1/de not_active Expired - Lifetime

Patent Citations (2)

Non-Patent Citations (2)

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