EP0052009B1 - Vorrichtung zum Sichern des Wärmetausches zwischen einem Gasstrom und einem Wärmetauscher - Google Patents

Vorrichtung zum Sichern des Wärmetausches zwischen einem Gasstrom und einem Wärmetauscher Download PDF

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Publication number
EP0052009B1
EP0052009B1 EP19810305324 EP81305324A EP0052009B1 EP 0052009 B1 EP0052009 B1 EP 0052009B1 EP 19810305324 EP19810305324 EP 19810305324 EP 81305324 A EP81305324 A EP 81305324A EP 0052009 B1 EP0052009 B1 EP 0052009B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
diaphragm
duct
gas flow
nozzles
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
Application number
EP19810305324
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English (en)
French (fr)
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EP0052009A3 (en
EP0052009A2 (de
Inventor
Ivan Bloomer
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.)
Haden Drysys International Ltd
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Haden Drysys International Ltd
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Filing date
Publication date
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Publication of EP0052009A2 publication Critical patent/EP0052009A2/de
Publication of EP0052009A3 publication Critical patent/EP0052009A3/en
Application granted granted Critical
Publication of EP0052009B1 publication Critical patent/EP0052009B1/de
Expired legal-status Critical Current

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Classifications

    • 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

Definitions

  • the present invention relates to apparatus for ensuring heat exchange between a gas flow and a heat exchanger.
  • the air exhausted from an industrial process or from an air conditioned building may be at a temperature either above or below the ambient temperature and this temperature difference represents energy which it is desirable to reclaim.
  • Air is supplied to paint spray booths, particularly where water-based paints are used, which is conditioned to a controlled temperature and humidity. This air is then exhausted to atmosphere. Large volumes of air must be conditioned with a consequent expenditure of energy and accordingly it is desirable to recover this energy from the exhaust air.
  • the heat exchanger coils contain the condenser fluid from a refrigeration plant and this condenser fluid is cooled by the exhaust air from a paint spray booth.
  • apparatus for ensuring heat exchange between a gas flow and a heat exchanger comprising a duct through which a flow of gas can be established, a heat exchanger mounted in the duct such that the gas flows therethrough, and means for spraying liquid within the duct, such as known from US-A-2 200 442.
  • This apparatus is characterised in that a diaphragm is mounted to extend across the duct upstream of the heat exchanger in the direction of gas flow, that a plurality of flow passages extend through said diaphragm and in that said flow passages define constrictions for the gas flow such that jets of gas are produced.
  • the jets of gas created by the constrictions are able to carry liquid into the heat exchanger because of their high velocity and accordingly the surfaces of the heat exchanger are thoroughly wetted. It would be wholly uneconomic to establish the total gas flow through the duct at a sufficiently high velocity to achieve a similar effect because of the power which would be required to establish such a high velocity gas flow.
  • the or some of the flow passages may converge in the direction of gas flow to increase the velocity of the jets and to minimise any subsequent flow contraction. Additionally and/or alternately the size of the flow passages may be variable such that the apparatus can be made responsive to changes in the performance required and/or to changes in variables of the system in which the apparatus is incorporated.
  • the duct extends vertically and the air is confined to flow upwardly through the duct.
  • a perforated diaphragm extends horizontally across the duct below the heat exchanger. The perimeter of the diaphragm is sealed to the duct. Accordingly, liquid which drains off the duct walls and off the heat exchanger collects over the whole area of the diaphragm. The jets of gas created through the perforations carry liquid collected on the plate into the heat exchanger and it is thereby ensured that the surfaces of the heat exchanger can be reliably wetted by liquid carried from the diaphragm by the gas flow.
  • the liquid is introduced into the duct by spraying, preferably from one or more nozzles within the duct.
  • nozzles Various configurations for the nozzles can be used.
  • one or more nozzles may be disposed beneath the diaphragm and directed upwardly towards the heat exchanger. Appropriate apertures must then be provided in the diaphragm and aligned with the nozzles.
  • one or more nozzles may be disposed above the heat exchanger and directed downwardly towards the heat exchanger. The number, configuration and position of the nozzles is chosen in dependence upon the heat transfer rate required, the acceptable gas pressure drop, and the size of the heat exchanger.
  • the heat exchanger is a coiled tube heat exchanger which is in two sections, a first main section and a second preliminary section.
  • the two sections are mounted in the duct with the main section spaced above the preliminary section.
  • the perforated diaphragm is mounted between the two sections and water spray nozzles are arranged to direct water towards the main section.
  • the perforated diaphragm thus acts to ensure thorough wetting of the main section. If required, additional spray nozzles may direct water onto the preliminary section. It has not been found necessary to provide an additional perforated diaphragm below the preliminary section but such an additional diaphragm could, of course, be provided.
  • the two coil sections are connected together and are part of a common heat transfer medium circuit.
  • the heat transfer medium flows in the direction opposite to the direction of the air flow in accordance with well-known principles.
  • FIG. 1 shows a longitudinal section of apparatus for ensuring heat exchange between a gas flow and a heat exchanger.
  • the apparatus comprises a duct 2 defined by substantially vertically extending walls 4, preferably made of galvanised sheet-metal.
  • the duct 2 has a rectangular cross-section although a duct of any required cross-section may be provided.
  • a main heat exchanger 6 is mounted to extend across the duct 2.
  • This heat exchanger 6 is constructed from a coiled tube 8 and fins 10 are provided on the tube 8 in known manner.
  • the coils of the tube 8 extend through the duct walls 4 and are supported in supports 12 fixed to the outer surface of the walls 4.
  • the heat exchanger 6 efficiently utilizes the internal area of the duct 2.
  • One end 14 of the tube 8 is the inlet for a heat transfer medium and the other end 16 of the tube 8 is the outlet for the heat transfer medium.
  • a preliminary heat exchanger 18 is mounted to extend across the duct 2 below and spaced from the main heat exchanger 6.
  • This preliminary heat exchanger 18 is similarly constructed from a coiled tube 8' provided with fins 10' and the coils of the tube 8' extend through the duct walls 4 and are supported in supports 12'.
  • One end 20 of the coiled tube 8' is the inlet for the fluid transfer medium and is connected to the outlet 16 of the main heat exchanger 6.
  • the other end 22 of the coiled tube 8' is the outlet for the heat transfer medium.
  • a rectangular perforated plate or diaphragm 24 is mounted to extend across the duct 2 between and spaced from the two heat exchangers 6 and 18.
  • the diaphragm 24 is supported by a rectangular angle iron frame 26 fixed to the inner surface of the duct walls 4, for example, by welding.
  • the whole perimeter of the diaphragm 24 is welded or otherwise sealed to the frame 26.
  • the diaphragm 24 is made of a material and of a thickness such that it is substantially rigid and remains level.
  • the diaphragm may be made of galvanised sheet-metal. If necessary supports (not shown) may be arranged beneath the diaphragm 24.
  • An array of holes 27 are regularly spaced over the total surface area of the diaphragm 24. Preferably, the holes 27 are sized and spaced such that the holes make up approximately 25% of the surface area of the diaphragm.
  • a pipe 28 having an inlet 30 extends across the duct 2 above the main heat exchanger 6.
  • a plurality of spray nozzles 32 each facing the heat exchanger 6 are provided on the pipe 28.
  • a pipe 34 having an inlet 36 extends across the duct 2 below the perforated diaphragm 24.
  • the pipe 34 has a plurality of upwardly directed spray nozzles 38 and a plurality of downwardly directed spray nozzles 40 each of which is aligned with a respective upwardly directed nozzle 38.
  • Each of the nozzles 38 extends through a respective aperture 27 in the diaphragm 24.
  • the duct 2 is arranged such that gas, for example, air from which energy is to be recovered, flows upwardly therethrough as indicated by arrow A.
  • gas for example, air from which energy is to be recovered
  • the duct 2 can be connected to receive the exhaust air from a paint spray booth.
  • Heat transfer medium for example, glycol
  • the transfer medium enters inlet 14 and flows through the coil 8 to the outlet 16, it subsequently flows into the coil 8' through inlet 20 and then flows out of the outlet 22 after flowing through the coil 8'.
  • the heat transfer medium flows in the direction opposite to the direction of the air flow through the duct 2.
  • the heat transfer medium will be either heated or cooled by the air flow and the energy thus imparted thereto can then be used as required.
  • the exhaust air is cold it can be used to cool the condenser fluid from a refrigerator.
  • This condenser fluid will be the heat transfer medium flowing through the heat exchangers 6 and 18.
  • the heat transfer rate can be improved by wetting the coils 6 and 18. Accordingly, in operation a liquid, such as water, is fed to the pipes 28 and 34 such that the nozzles 32, 38 and 40 spray water over the coiled tubes 8 and 8'.
  • a liquid such as water
  • the water sprayed by the nozzles 32 and 38 onto the main heat exchanger 6 will flow over the heat exchanger 6 and the duct walls 4 and will collect on the perforated diaphragm 24. As the air flows through the holes 27 in the diaphragm high velocity jets of air will be created. These jets of air carry water from the plate into the heat exchanger 6 and efficiently wet the surfaces of the coiled tube 8 and fins 10.
  • each row of nozzles could be replaced by an array of nozzles extending transversely across the duct.
  • one or each row of nozzles could be replaced by a single nozzle.
  • suitable apertures must be provided in the diaphragm 24 which are aligned with the nozzles.
  • each nozzle 38 extends through one of the holes 27 in the perforated diaphragm 24.
  • apertures for the nozzles may additionally be provided in the diaphragm 24.
  • Figure 2 shows a plan view of an embodiment of the perforated diaphragm 24 fixed into the duct by an angle iron frame 26 welded to the duct walls 4.
  • the plate 24 shown in Figure 2 is used where only a single spray nozzle 38' facing upwardly towards the main heat exchanger 6 is provided in place of the row of nozzles 38 shown in Figure 1.
  • the diaphragm 24 has a central aperture 42 provided therein and aligned with the nozzle 38'.
  • FIG. 3 illustrates a further embodiment of the invention and indicates the circuits for the water and the heat transfer medium.
  • a single heat exchanger 44 is mounted to extend across the duct 2.
  • the heat exchanger 44 is a coiled tube construction and has an inlet 46 and an outlet 48 for the heat transfer medium, for example, glycol.
  • the glycol fed from the heat exchanger 44 is fed to a device 50, for example, a refrigerator condenser, where the energy thereof can be utilized.
  • the glycol is then returned to a reservoir 52 from which it is pumped by pump 54 to the inlet 46.
  • a single nozzle 56 is arranged beneath the perforated diaphragm 24.
  • This nozzle 56 which faces the heat exchanger 44, is connected to receive water from the mains by a pipe 58 including a pump 60.
  • FIG. 4 shows a further embodiment of the apparatus in which the single coiled tube heat exchanger 44 is mounted to extend across a vertically extending duct 2.
  • the perforated diaphragm 24 is mounted to extend across the duct upstream of the heat exchanger 44 but water is sprayed onto the heat exchanger 44 from a single spray nozzle 62 positioned above the heat exchanger 44 and facing downwardly.
  • this embodiment will operate substantially as described above as water flowing downwardly over the heat ' exchanger 44 will collect on the diaphragm 24 and will then be carried by the jets of air created by the plate 24 into the heat exchanger to efficiently wet the surfaces thereof.
  • Figures 5 and 6 show further embodiments of the apparatus in which the duct 2 is arranged to extend substantially horizontally.
  • an additional, vertically extending duct 64 is connected with the main duct and one or more spray nozzles 66 fed by a pipe 68 are mounted in the additional duct. Accordingly, water is sprayed downwardly over the heat exchanger 44.
  • the perforated diaphragm 24 is mounted to extend across the duct 2 spaced from and upstream of the heat exchanger 44 in the direction of air flow. In this embodiment, water will not collect on the diaphragm 24 but the diaphragm 24 will still create jets of air flowing across the surfaces of the heat exchanger 44. These jets of air will pick up water flowing over the heat exchanger and thereby ensure that the surfaces of the heat exchanger 44 are efficiently wetted.
  • one or more nozzles 66 are arranged upstream of the diaphragm 24 and aligned with apertures therein.
  • Figure 7 shows a plan view of the perforated diaphragm 24 which is fitted tightly to the duct walls 4 and fixed thereto, for example, by welding or by the use of a sealant. The joint is then sealed by applying a strip 70 of a waterproof sealant.
  • the perforated diaphragm 24 is shown as being provided with a series of equally sized circular holes 27 equidistantly spaced over the whole area of the diaphragm 24.
  • differently shaped holes for example, polyhedral holes, may be provided and the size and spacing of the holes may be chosen as required.
  • Figure 8 shows a plan view of an alternative diaphragm 124 which is perforated by a series of elongate apertures 127.
  • FIGS 9 and 9A show a plan view and a section of an alternative diaphragm 224 having a series of elongate orifices 227. Each of the orifices 227 has been pressed from the material of the diaphragm such that a flange 228 extending substantially perpendicular to the plane of the diaphragm 224 has been formed. As is clearly shown in Figure 9A each flange 228 defines a convergent air flow passage 229.
  • the diaphragm 224 is arranged such that the flow passage 229 converges in the direction of air flow so that a contracting contour is presented to the air flow.
  • the contour is arranged to minimise any flow contraction of the air jets once they have left the flow passages 229.
  • Figures 10 and 10A show a plan view and a section of a diaphragm 324 having a number of rigid strips 326 defining slots 327 therebetween.
  • the longitudinally extending edges of the strips 326 extend within the plane of the diaphragm 324.
  • Figures 11 and 11 A show a plan view and a section of an alternative diaphragm 424 having slots 427 defined by strips 426.
  • the longitudinally extending edges of the strips 426 carry flanges 428 extending substantially perpendicular to the plane of the diaphragm 426 and defining convergent flow passages 429.
  • the diaphragm 426 is arranged such that the flow passages 429 converge in the direction of air flow.
  • the number and width of the strips 326, 426 can be chosen in accordance with the required area of flow passages for the air. These embodiments also enable one or more flow zones to be defined such that air flow can be directed onto one or more selected areas on the face of the heat exchanger. In this manner advantage can be taken of varying temperature differences between the air flow and different areas of the heat exchanger coil.
  • the diaphragm 524 is provided with a series of circular apertures 527.
  • a cylindrical wall 528 is fixed, for example, by welding, to the edge of each aperture to define elongate flow passages 529 extending perpendicularly relative to the plane of the diaphragm.
  • the diaphragm should be spaced from the heat exchanger by a predetermined distance.
  • the heat exchanger coil has a cross-sectional area of the order of 2.2 m 2 it is preferred that the diaphragm should be spaced therefrom by 100-120 mm.
  • the diaphragm 524 can be mounted at a greater spacing from the heat exchanger and the length of the walls 528 chosen such that the free ends thereof lie in a plane situated at the required distance from the heat exchanger.
  • Figures 13 and 13A show an embodiment of a diaphragm which can be used to adjustably control the air flow.
  • the diaphragm 624 of Figure 13 comprises a number of elongate rigid strips 626 extending substantially parallel to each other transversely of the diaphragm 624.
  • a spindle 630 is rigidly attached to each end of each strip 626 and each spindle 630 is pivotable in a respective bearing 632 fixed in the angle frame 26.
  • the strips 626 form pivotable damper blades.
  • a transversely extending fixed strip 634 is also provided at each end of the diaphragm 624 and is attached to the angle frame 26.
  • the blades are pivoted to project from the plane of the diaphragm such that air flow passages 629 are defined between adjacent strips. Every alternate air flow passage 629 will converge in the direction of the air flow, as can be seen in Figure 13A, and thus produce high velocity jets of air. Adjustment of the position of the damper blades will adjust the size of the air flow passages and thus the velocity of the jets of air and hence the thermal duty.
  • FIGS 14 and 14A show a further embodiment of a diaphragm 724 which can be used when variations in the velocity of the jets of air is required.
  • the diaphragm 724 comprises two plates 721 and 722 mounted one on top of the other. The periphery of each plate 721, 722 is received within a channel section frame 726 which is attached to the duct. The top plate 721 is fixed to the frame 726, whilst the lower plate 722 is supported by the frame 726 so as to be adjustable relative to the top plate 721.
  • a number of bolts 730 are arranged around the frame 726 for urging the frame 726 into contact with the lower plate 722.
  • Each of the plates 721 and 722 is provided with an array of holes 727 over its area.
  • the holes of one plate substantially correspond in both size and distribution to the holes of the other plate. It will be apparent that as the lower plate 722 is moved relative to the top plate 721 the air flow passages defined by the holes 727 will be varied in size.
  • a central aperture 42 is provided therein for alignment with a water spray nozzle.
  • this central aperture 42 can be omitted and the or each spray nozzle aligned with the apertures or slots provided in the diaphragm.
  • the diaphragm is illustrated as being fixed to the duct wall by an angle iron. Of course, other fixing means can be used as required.

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

Claims (17)

1. Vorrichtung zur Sicherstellung eines Wärmeaustausches zwischen einem Gasstrom und einem Wärmeaustauscher, bestehend aus einer Leitung (2), durch welche ein Gasstrom (A) geleitet werden kann, und einen Wärme- lauscher (6, 44), der so in die Leitung eingebaut ist, daß das Gas hindurchströmt, sowie Vorrichtungen (32, 38, 40, 56, 62, 66) für das Versprühen von Flüssigkeit innerhalb der Leitung, dadurch gekennzeichnet, daß eine Membran (24, 124, 224, 324, 424, 524, 624, 724) befestigt ist, welche sich schwer durch die Leitung erstreckt und in Richtung des Gasstromes vor dem Wärmetauscher angeordnet ist, daß eine Vielzahl von Stromdurchlässen (229, 429, 529, 629) diese Membran durchdringen und daß diese Stromdurchlässe Verengungen für den Gasstrom bilden, so daß Gasstrahlen erzeugt werden.
2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß wenigstens einer (229, 429, 629) dieser Stromdurchlässe in Richtung des Gasstromflusses konvergiert.
3. Vorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß die Membran Mittel (626, 632; 721, 722) zur Größenverstellung der Stromdurchlässe umfaßt.
4. Vorrichtung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die Membran eine steife Platte mit mehreren Öffnungen (27, 127, 227, 327, 427, 527, 727) umfaßt, welche sie durchgreifen.
5. Vorrichtung nach Anspruch 4, dadurch gekennzeichnet, daß die Öffnungen in der Platte im wesentlichen 25% der gesamten Plattenfläche einnehmen.
6. Vorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß die Membran Abstand vom Wärmeaustauscher (6, 18, 44) aufweist.
7. Vorrichtung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß die Sprühvorrichtung für Flüssigkeit in der Leitung ein oder mehrere vor der Membran in Richtung des Gasstromes auf den Wärmeaustauscher (6, 44) hingerichtete Düsen (38, 56, 66) umfaßt und daß in der Membran eine oder mehrere Öffnungen (27, 42, 127, 227, 327, 427, 527, 627, 727) vorgesehen sind und die Düsen jeweils mit der entsprechenden Öffnung gefluchtet sind.
8. Vorrichtung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß die Vorrichtung zum Sprühen von Flüssigkeit in der Leitung eine oder mehrere in die Leitung eingebaute Düsen umfaßt, die durch eine entsprechende Öffnung, welche in der Membran vorgesehen ist, sich erstrecken, wobei die Düse oder die Düsen auf den Wärmetauscher (6, 44) gerichtet ist bzw. sind.
9. Vorrichtung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß die Vorrichtung zum Sprühen von Flüssigkeit in der Leitung eine oder mehrere in die Leitung zwischen der Membran und dem Wärmeaustauscher (6, 44) eingebaute Düsen umfaßt, wobei die Düse oder wenigstens einige der Düsen auf den Wärmeaustauscher (6, 44) gerichtet sind.
10. Vorrichtung nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, daß die Vorrichtung zum Sprühen von Flüssigkeit in der Leitung eine oder mehrere, dem Wärmetauscher (6, 44) in Richtung des Gasstromes nachgeschaltete und auf den Wärmetauscher gerichtete Düsen (32) umfaßt.
11. Vorrichtung nach einem der Ansprüche 1 bis 10, wobei die Leitung (2) durch sich senkrecht erstreckende Wände (4) begrenzt ist, dadurch gekennzeichnet, daß die Membran (24, 124, 224, 324, 424, 524, 624, 724) im wesentlichen starr ist und senkrecht zu den Wänden (4) der Leitung verläuft und der Umfang der Membran gegenüber den Wänden (4) abgedichtet ist und daß die Vorrichtung zur Erzeugung eines Gasstromes so angeordnet ist, daß sie einen durch die Leitung nach oben gerichteten Gasstrom (A) erzeugt, wobei die Membran unter dem Wärmetauscher (6, 44) angebracht ist.
12. Vorrichtung nach einem der Ansprüche 1 bis 11, wobei die Leitung (2) durch horizontal sich erstreckende Wände begrenzt ist, dadurch gekennzeichnet, daß die Membran (24, 124, 224, 324, 424, 524, 624, 724) im wesentlichen starr ist und senkrecht in Bezug auf die Wände der Leitung verläuft..
13. Vorrichtung nach Anspruch 12, dadurch gekennzeichnet, daß die Vorrichtung zum Sprühen von Flüssigkeit in der Leitung eine oder mehrere oberhalb des Wärmeaustauschers (44) montierte und nach unten auf den Wärmeaustauscher zu gerichtete Düsen (66) umfaßt.
14. Vorrichtung nach einem der Ansprüche 1 bis 13, dadurch gekennzeichnet, daß ein zweiter Wärmeaustauscher (18) so in die Leitung eingebaut ist, daß das Gas hindurchströmt, wobei dieser zweite Wärmeaustauscher mit Abstand vom ersten Wärmeaustauscher (6, 44) in Richtung des Gasstromes vor diesem eingebaut ist und die Membran sich zwischen dem ersten und dem zweiten Wärmeaustauscher befindet.
15. Vorrichtung nach Anspruch 14, dadurch gekennzeichnet, daß der erste und der zweite Wärmeaustauscher mit einer gemeinsamen Leitung zur Versorgung mit dem Wärmeübertragungsmedium verbunden sind.
16. Vorrichtung nach einem der Ansprüche 14 oder 15, dadurch gekennzeichnet, daß jeder der genannten ersten und zweiten Wärmeaustauscher ein gewundenes Rohr (8, 8') aufweist und daß an dem gewundenen Rohr eines jeden Wärmeaustauschers Rippen (10, 10') vorgesehen sind.
17. Vorrichtung nach Anspruch 16, dadurch gekennzeichnet, daß die Vorrichtung zum Sprühen von Flüssigkeit in der Leitung zudem eine oder mehrere, der Membran vorgeschaltete und auf auf den zweiten Wärmeaustauscher gerichtete Düsen (40) umfaßt.
EP19810305324 1980-11-10 1981-11-10 Vorrichtung zum Sichern des Wärmetausches zwischen einem Gasstrom und einem Wärmetauscher Expired EP0052009B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US20547980A 1980-11-10 1980-11-10
US205479 1988-06-13

Publications (3)

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EP0052009A2 EP0052009A2 (de) 1982-05-19
EP0052009A3 EP0052009A3 (en) 1982-11-10
EP0052009B1 true EP0052009B1 (de) 1984-06-13

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EP (1) EP0052009B1 (de)
JP (1) JPS57108590A (de)
DE (1) DE3164224D1 (de)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5435382A (en) * 1993-06-16 1995-07-25 Baltimore Aircoil Company, Inc. Combination direct and indirect closed circuit evaporative heat exchanger
US5946932A (en) * 1998-06-03 1999-09-07 Wang; Huai-Wei Multistage condensing structure
JP4897302B2 (ja) * 2006-02-06 2012-03-14 和彦 岩崎 破魔矢の室内装飾台
CN104684344A (zh) * 2013-11-29 2015-06-03 国际商业机器公司 Pcm冷却设备,冷却系统和控制该系统的方法和单元

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2200442A (en) * 1938-06-22 1940-05-14 Robert B P Crawford Fluid cooling
US2504149A (en) * 1946-12-19 1950-04-18 Niagara Blower Co Evaporative heat exchanger
US3785625A (en) * 1971-05-19 1974-01-15 Baltimore Aircoil Co Inc Injector type evaporative heat exchanger
US4060024A (en) * 1976-10-28 1977-11-29 Goodman Manufacturing Corporation Damper assembly

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DE3164224D1 (en) 1984-07-19
JPS57108590A (en) 1982-07-06
JPH0127358B2 (de) 1989-05-29
EP0052009A3 (en) 1982-11-10
EP0052009A2 (de) 1982-05-19

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