EP0269634B1 - Vorrichtung zur indirekten verdampfungskühlung - Google Patents

Vorrichtung zur indirekten verdampfungskühlung Download PDF

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Publication number
EP0269634B1
EP0269634B1 EP86905456A EP86905456A EP0269634B1 EP 0269634 B1 EP0269634 B1 EP 0269634B1 EP 86905456 A EP86905456 A EP 86905456A EP 86905456 A EP86905456 A EP 86905456A EP 0269634 B1 EP0269634 B1 EP 0269634B1
Authority
EP
European Patent Office
Prior art keywords
duct system
duct
water
cooling
cooling air
Prior art date
Legal status (The legal status 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 status listed.)
Expired - Lifetime
Application number
EP86905456A
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English (en)
French (fr)
Other versions
EP0269634A1 (de
Inventor
Per Norbäck
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Carl Munters AB
Original Assignee
Carl Munters AB
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
Application filed by Carl Munters AB filed Critical Carl Munters AB
Publication of EP0269634A1 publication Critical patent/EP0269634A1/de
Application granted granted Critical
Publication of EP0269634B1 publication Critical patent/EP0269634B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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 indirect evaporative cooling of a supply air flow
  • a heat exchange unit made up from layers with ducts between the layers, the ducts being divided into two separate duct systems, where one system has the supply air flow passing through it and the other the cooling air flow, cooling being substantially achieved by evaporation of water in the other duct system, whereby means supplying water to the second duct system are disposed on the upper side of the heat exchange unit, so that the water flows vertically downwards in this duct system.
  • SE-B-383 777 an apparatus of this kind is disclosed, in which means supplying water to the second duct system are disposed on the upper side of the unit, so that the water flows vertically downwards in this duct system.
  • US-A-3 305 010 is disclosed a plate type heat exchanger apparatus in which two fluids of different temperatures are introduced at opposite ends of the apparatus to flow counter to one another between superposed stacked plate and fin elements.
  • this apparatus has no means for supplying water to one of the duct systems in order to provide cooling.
  • the invention has for the main object to provide an apparatus of the kind mentioned in the introduction with a configuration such that good heat transfer and favourable flow conditions are afforded in its use as an evaporative heat exchanger, the configuration especially enabling the supply air flow to have a horizontal flow direction for the apparatus readily to be incorporated in ventilation plants, where the normal duct system is horizontal.
  • the heat exchanger unit 10 illustrated in Figure 1 is used as an indirect heat exchanger for a supply air flow flowing substantially horizontally through the unit 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 unit 10 the supply air flow 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 airflow.
  • the unit 10 may be made up from a plurality of flat plates 11-15, these being put together with flange-like stiffening and surface magnifying means therebetween, as illustrated in Figure 5, these means being in the embodiment shown corrugated metal sheets or foils 16.
  • the corrugations in the sheets 16 constitute the ducts for the supply air which is to be cooled in the contact body 10, the sheets 16 being oriented with their corrugations extending 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 supply 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 intrinsically 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 cooling air flow shall pass.
  • the walls of the gaps 18 are wetted in a manner known per se.
  • the 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.
  • the 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 supply 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 independently.
  • the amount of cooling air is also normally less than that of the supply air, due to the evaporative effect.
  • the flanges of the stiffening means or corrugated sheets 16, included in the sandwich element 12-16 constitutes a large heat transfer surface which is brushed over by the passing supply air flow.
  • the intrinsically 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 corrugated 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 be 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 ventilation system such that the supply 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 flow, e.g. 10-50%, of this cooled supply air flow is returned as a cooling air flow in counterflow to the supply air flow through the second duct system 18, where the supply 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 flow 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 supply air flow is passed to the supply 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 supply air flow 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 flow is turned to enter the ducts 18 to form the cooling air flow, 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.
  • FIG. 3 The flow of the cooling air flow in a duct 18 is depicted in Figure 3, showing that the cooling air flow flows from the right side of the body to the outlet 26.
  • the other duct system includes ducts 18 extending 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 flow 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.
  • intermediate walls 34 are arranged between the jets 24, as seen in Figure 4.
  • the body is provided with a collection trough 36 for excess water. If so desired, recirculation of water from the trough to the jets 24 can be arranged.
  • intermediate walls 35 are arranged 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 supply air flows in the ducts 16.
  • cooling air flow 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 negative effect on the cooling.
  • the cooling is namely dependent 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 flows 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 flows also get an increased temperature, which further enfeebles 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 disposed 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 supply air flow will be greater than the outlet 26 for the cooling air flow. This difference in size can vary and is dependent on the size of the air flows.
  • 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 supply air flow duct system 16 could comprise the entire vertical side with the cooling air flow being taken out vertically upwards.
  • the illustrated 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 supply air can be supplied to the contact bodies 10 via the inlets 28 and the cooling air flow 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 advantage with this implementation is that water can be commonly 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 systems 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)

Claims (10)

1. Anordnung zum indirekten evaporativen Kühlen eines Nutzluftstromes, mit einem Wärmetauscher (10), aufgebaut aus Schichten mit dazwischen liegenden Kanälen (16, 18), wobei die Kanäle in zwei getrennte Kanalsysteme aufgetelt sind, wovon das eine System (16) von einem Versorgungsluftstrom und das zweite von einem Kühlluftstrom durchströmt wird und das Kühlen hauptsächlich durch Evaporation von Wasser im zweiten Kanalsystem (18) erfolgt, wobei Mittel (24) zur Versorgung des zweiten Kanalsystems mit Wasser an der Oberseite des Wärmetauscher so angebracht sind, daß das Wasser senkrecht nach unten in diesem Kanalsystem (18) fließt, dadurch gekennzeichnet, daß die kanalbildenden Mittel (16, 32) in beiden Kanalsystemen (16, 18) so angebracht sind, daß die beiden Versorgungs- bzw. Kühlluftströme sich horizontal bewegen, daß die Einlässe und Auslässe der beiden Kanalsysteme (16, 18) so anbracht sind, daß die Versorgungsluft- und Kühlluftströme einander entgegengesetzt sind, sowie daß Zwischenwände (34, 35) oben und unten so am Wärmetauscher angebracht sind, daß sie Kühlluft daran hindern, zur Wasserversorgung (24) oder zum Wassersammler (36) an der Bodenseite des Wärmetauschers abgelenkt zu werden.
2. Anordnung nach Anspruch 1, dadurch gekennzeichnet, daß der Auslaß des ersten Kanalsystems (16) und der Einlaß des zweiten Kanalsystems (18) angrenzend an und in Verbindung mit einander so angebracht sind, daß der Kühlluftstrom zum zweiten Kanalsystem als ein Teil der das erste Kanalsystem verlassenden Luft abgezweigt wird.
3. Anordnung nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß eine senkrechte Seite (26, 28) des Wärmetauschers (10) mit einer dreieckigen Spitze ausgeführt ist, wobei die zur Spitze führenden Seiten als Einlaß (28) zum ersten Kanalsystem (16) bzw. als Auslaß (26) vom zweiten Kanalsystem (18) ausgeführt sind.
4. Anordnung nach Anspruch 3, dadurch gekennzeichnet, daß die an die Spitze angrenzenden Seiten (26, 28) verschieden lang sind uns daß die längere Seite (28) die öffnung für den Frischluftstrom ist.
5. Anordnung nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß der Wärmetauscher aus einer Mehrzahl von flachen Platten (12, 13) mit dazwischen liegenden flanschähnlichen versteifenden und die Oberfläche vergrößernden Mitteln (16) gefertigt ist, die zusammen eine Vielzahl von eigensteifen Tafeln bilden, die mit Hilfe von Abstandshaltern (32) den Wärmetauscher (10) bilden, wobei die Abstandshalter (32) das zweite Kanalsystem (18) definieren, während die Paneele das erste Kanalsystem (16) umfassen.
6. Anordnung nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß das dreieckige Einlaßteil (28) des ersten Kanals (16) mit einem geringeren Durchflußwiderstand als der Rest des Systems ausgeführt ist.
7. Anordnung nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, daß der Auslaß (26) vom zweiten Kanalsystem (18) nach oben gerichtet ist.
8. Anordnung nach Anspruch 5, dadurch gekennzeichnet, daß die Abstandshalter (32) so geformt sind, daß die Kühlluft und das Wasser im wesentlichen unbehindert in zweiten Kanalsystem fließen, d.h. beispielsweise punktformig sind.
9. Anordnung nach Anspruch 5, dadurch gekennzeichnet, daß die Versteifungsorgane durch gewellte Platten (16) zwischen den ebenen Platten (12, 13) gebildet sind, sowie daß die gewellten Platten mit den Wellenscheiteln in derselben Horizontalebene liegen.
10. Anordnung nach einem vorstehenden Ansprüche, dadurch gekennzeichnet, daß eine Mehrzahl von Wärmetauschern (10) aufeinander gestapelt sind, wobei die Wasserzufuhr (24) am Gipfel des Stapels zum zweiten Kanalsystem und der Wassersammler (36) am Boden des Stapels gemeinsam für sämtliche Wärmetauscher (10) im Stapel sind.
EP86905456A 1985-08-16 1986-08-14 Vorrichtung zur indirekten verdampfungskühlung Expired - Lifetime EP0269634B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE8503854 1985-08-16
SE8503854A SE460151B (sv) 1985-08-16 1985-08-16 Anordning foer indirekt evaporativ kylning

Publications (2)

Publication Number Publication Date
EP0269634A1 EP0269634A1 (de) 1988-06-08
EP0269634B1 true EP0269634B1 (de) 1990-12-27

Family

ID=20361124

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EP86905456A Expired - Lifetime EP0269634B1 (de) 1985-08-16 1986-08-14 Vorrichtung zur indirekten verdampfungskühlung

Country Status (5)

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EP (1) EP0269634B1 (de)
AU (1) AU6333486A (de)
DE (1) DE3676707D1 (de)
SE (1) SE460151B (de)
WO (1) WO1987001188A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104204685A (zh) * 2012-02-17 2014-12-10 科普麦恩有限公司 用于冷却和/或用于热回收的设备

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FI88431C (fi) * 1989-08-22 1993-05-10 Ilmateollisuus Oy Foerfarande och kylarrangemang foer avkylning av en byggnad
AUPM755094A0 (en) * 1994-08-18 1994-09-08 F F Seeley Nominees Pty Ltd Intensification of evaporation and heat transfer
RU2692180C1 (ru) * 2018-07-03 2019-06-21 Акционерное общество "Группа Машиностроительных Заводов "Химмаш" Способ косвенно-испарительного охлаждения воздуха и устройство для его осуществления
WO2022243713A1 (en) 2021-05-18 2022-11-24 Poly-Rek D.O.O. Climate control systems with indirect and direct adiabatic cooling

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3305010A (en) * 1965-04-13 1967-02-21 United Aircraft Prod Plate and fin heat exchanger
SE383777B (sv) * 1973-07-18 1976-03-29 Munters Ab Carl Sett och anordning for kylning av luft

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104204685A (zh) * 2012-02-17 2014-12-10 科普麦恩有限公司 用于冷却和/或用于热回收的设备

Also Published As

Publication number Publication date
SE460151B (sv) 1989-09-11
DE3676707D1 (de) 1991-02-07
SE8503854L (sv) 1987-02-17
WO1987001188A1 (en) 1987-02-26
SE8503854D0 (sv) 1985-08-16
AU6333486A (en) 1987-03-10
EP0269634A1 (de) 1988-06-08

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