EP0730131A1 - Vorrichtung zum Kühlen einer Flüssigkeit oder Kondensieren von Dampf - Google Patents

Vorrichtung zum Kühlen einer Flüssigkeit oder Kondensieren von Dampf Download PDF

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Publication number
EP0730131A1
EP0730131A1 EP96490012A EP96490012A EP0730131A1 EP 0730131 A1 EP0730131 A1 EP 0730131A1 EP 96490012 A EP96490012 A EP 96490012A EP 96490012 A EP96490012 A EP 96490012A EP 0730131 A1 EP0730131 A1 EP 0730131A1
Authority
EP
European Patent Office
Prior art keywords
exchanger
tubes
fins
auxiliary liquid
gas flow
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.)
Withdrawn
Application number
EP96490012A
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English (en)
French (fr)
Inventor
Didier Lemaire
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.)
Kelvion SAS
Original Assignee
GEA Erge Spirale and Soramat SAS
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 GEA Erge Spirale and Soramat SAS filed Critical GEA Erge Spirale and Soramat SAS
Priority to EP96490012A priority Critical patent/EP0730131A1/de
Publication of EP0730131A1 publication Critical patent/EP0730131A1/de
Withdrawn legal-status Critical Current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 a heat exchanger device and more particularly for cooling a fluid, generally a liquid, or for condensing a vapor. It relates more precisely to a cooling or condensing device in which the exchange is carried out by mechanically ventilated atmospheric air.
  • the exchange function is performed by mechanically ventilated atmospheric air; the corresponding device is an air cooler.
  • the exchange surface is watered so that the heat of the primary fluid both warms the surrounding air and evaporates part of the irrigation water.
  • the device consists of what is commonly known as a closed circuit cooling tower.
  • the heat exchanger is composed of a battery of tubes with transverse fins; spray nozzles spray the external surface of the tubes and the fins with an auxiliary liquid; means are provided to ensure natural or forced circulation of a gas flow through the exchanger.
  • the battery of tubes consists of a set of two tube alignments, said alignments being arranged horizontally, the spray nozzles are placed above said tubes projecting the auxiliary liquid from top to bottom, while the gas flow enters in the device by the lateral and lower sides thereof, enters the exchanger against the current relative to the direction of the sprayed auxiliary liquid.
  • this first embodiment has the disadvantage that the air flow is thwarted by the presence, against the current, of the sprayed auxiliary liquid. This has the effect of increasing the pressure drop and necessitating decreasing the speed of passage of the air.
  • the two alignments of the tubes of the heat exchanger are arranged vertically, along lateral inlets, formed in the lower parts of the device.
  • the spray nozzles are arranged opposite and upstream of the exchanger with respect to the direction of the gas flow. This gas flow which enters the device through its lateral openings goes up towards the upper part of it.
  • this second embodiment has the drawback that the distribution of the auxiliary liquid which is sprayed on the tubes of the exchanger exhibits very great heterogeneity according to the position of each tube.
  • the tubes which are in the upper part of the exchanger are sprinkled exclusively with the auxiliary liquid coming from the nozzles immediately opposite; on the other hand, the tubes arranged in the lower part are watered not only by the liquid coming from the nozzles immediately opposite but also by the liquid flowing naturally from the tubes arranged above.
  • the goal that the applicant has set is to propose a device for cooling a fluid or condensing a vapor, which achieves this combination while overcoming the aforementioned drawbacks.
  • the device of the invention which in known manner comprises a heat exchanger composed of a battery of parallel tubes and with transverse fins, nozzles for spraying an auxiliary liquid on the external surface of the tubes and fins, and mechanical means for forming a gas flow.
  • the bank of tubes of the exchanger is inclined at an angle ⁇ of 5 to 60 ° relative to the vertical, the spray nozzles being arranged above the exchanger and the gas flow having a direction substantially horizontal, so as to first cross the sprayed auxiliary liquid before entering the exchanger.
  • FR.A.2 096 556 describes an indirect type evaporative heat exchanger in which the tube bundle has a slight inclination, but it is an exchanger which differs profoundly from that of the invention. It does not have mechanical means for forming a gas flow, the latter being created by the projection of air into the divergent-shaped duct of the exchanger; the air flow is a function of the water flow injected into the exchanger.
  • the tubes are smooth and not with transverse fins. The inclination of the tube bundle is intended to ensure that the bundle is completely wetted over its entire surface and over its entire depth.
  • the transverse fins are in vertical planes.
  • a high angle ⁇ between 30 and 60 ° has the drawback of increasing the pressure drops, due to the deflection of the air flow in the tube bundle, as will be explained in the example described. It is therefore preferable to aim for an angle ⁇ of lower value, between 5 and 30 or 35 °.
  • the spraying conditions are such that the average diameter of the sprayed drops is less at 120 micrometers.
  • the drops of smaller dimensions having a higher wettability and it is possible to obtain a continuous, homogeneous film of smaller thickness on the exchange surface of the exchanger, which limits the amount of liquid that drips.
  • the thickness of the film for a better exchange yield must be as small as possible.
  • the quantity of liquid evaporated relative to the quantity sprayed is increased being, of the order of 10 to 20%, which has the incidental advantage of limiting the subsequent treatments of liquid to be recycled.
  • each spray nozzle is a pyramid projection nozzle, which is directed perpendicular to the general direction of the battery of tubes, the arrangement of the spray nozzles being determined so as to produce a homogeneous projection of the auxiliary liquid over the entire surface of the 'exchanger.
  • the density of the sprayed auxiliary liquid varies according to the pitch of the transverse fins and according to the thickness of the liquid film which is desired at the surface of these transverse fins.
  • the liquid film must moreover be homogeneous over the entire exchange surface.
  • the surface condition of the fins, of the tubes, and the quality of the liquid are parameters which influence the thickness of the film and therefore the density of the auxiliary liquid.
  • the density of the auxiliary liquid projected by the spray nozzles is between 0.5 and 2.6 m 3 / hm 2 of front section of the exchanger.
  • the front section of the exchanger is called the projection of the surface of the exchanger in the plane perpendicular to the direction of the gas flow.
  • the inclination of the bundle of tubes is such that one of the diagonals of each transverse fin is substantially vertical. Since the distribution of the tubes on a given fin is a symmetrical distribution with respect to such a diagonal, this particular arrangement allows a flow of the liquid film on the two faces of each fin which is equally distributed, which contributes to the desired homogeneity. In conventional constructions of tubular bundles with transverse fins, the width and height of each fin is such that the angle of inclination ⁇ is then between 5 and 35 °.
  • the exchanger tubes are provided with internal means for intensifying the exchange.
  • These may in particular be internal fins of low height, in particular from 0.2 to 0.3 mm. It can also be a wick-type structure fixed to the internal wall of the tube, for example longitudinal linear fibers held in place by helical threads or alternatively random wicks or wicks made of metallic fabric .
  • the means for forming the gas flow consist of a helical fan with a motor at the end of the shaft, the air speed in the front section of the exchanger being between 3.0 and 4, sm / s.
  • the device 1 for cooling a fluid or condensing a vapor uses, for the exchange function, both mechanically ventilated atmospheric air and an auxiliary liquid which evaporates partially on contact with the surface of exchange.
  • the device 1 comprises a chamber 2 with, for the passage of the air flow, an inlet 3 and an outlet 4 which are arranged opposite one another so that the general direction of the air flow has a horizontal direction.
  • the air inlet 3 is provided with a deflector grid 5 preventing the introduction of solid particles inside the chamber 2.
  • the air outlet 4 is equipped, towards the outside of the chamber 2, with a motor-fan 6 which in the example illustrated is a helical fan.
  • a heat exchanger 7, with parallel tubes 8 and provided with transverse fins 9, is arranged obliquely inside the chamber 2, with an inclination which is between 5 and 60 ° relative to the vertical. In the example illustrated in FIG. 1, this angle of inclination ⁇ is 45 °.
  • the arrangement of the exchanger inside the chamber 2 is carried out so that all the air flow entering the chamber 2 must pass through the exchanger 7.
  • the device 1 is equipped with a sprinkler system comprising a motor-pump group 10, pipes 11 and spray nozzles 12.
  • the spray nozzles 12 are arranged between the inlet 3 and the exchanger 7; it is preferably pyramidal spray nozzles, which are arranged over the exchanger 7 so as to ensure a uniform projection of drops thereon.
  • two spray nozzles are shown, one ensuring the watering of the upper part of the exchanger while the other ensures the watering of the lower part, with little overlap between the two zones. watering.
  • a tank 13 for retaining the irrigation water, into which the non-evaporated water is discharged after having passed through the exchanger 7.
  • the motor-pump group 10 comes feed from the water contained in this tank 13. It is equipped with an overflow, a drain, a level regulation device, a deconcentration purge, a supply of make-up water and possibly an anti-freeze device. All of these elements are not shown in the figure.
  • a droplet separator 14 making the entire section of the chamber 2, at the level of the passage of the air flow.
  • the heat exchanger 7 is composed of a battery of tubes 8 parallel and aligned in six or eight rows 15 (of which only three are shown in Figure 1 for clarity).
  • the transverse external fins 9 are continuous flat fins for all the rows.
  • the tubes 8 of the rows are staggered, as illustrated in the figures.
  • the operation of the device 1 is as follows.
  • the air which is sucked in by the helical fan 4 penetrates through the inlet 3, any solid particles being retained by the grid 5, and leaves the device 1 through the outlet 4.
  • the air flow has a substantially horizontal direction (arrow F).
  • the air flow passes through the water coming from the spray nozzles 12 and is therefore loaded with moisture.
  • the direction of the air flow is modified, in accordance with the arrow F 'shown in the figure, the air flow then being perpendicular to the direction of the rows 15 of tubes 8.
  • the air flow returns to its initial horizontal direction.
  • the drops sprayed by the nozzles 12 on the external fins 9 create a film of water on the surface thereof.
  • the heat exchange causes partial evaporation of this film of water.
  • the rest falling back into the retention tank 13 is reinjected, thanks to the motor-pump group 10 into the spray nozzles 12.
  • the water thus evaporated is carried with the air flow to outlet 4.
  • the air flow which is almost completely or completely saturated with water vapor, carries droplets torn from the water film.
  • These droplets are trapped by the separator 14 which can, for example, consist of a set of juxtaposed plates and delimiting between them passages in baffles. The water coming from the separator 14 falls back into the tank 13.
  • the fluid to be cooled or the vapor to be condensed circulates inside the tubes 8 of the exchanger. It is the primary fluid. It is this primary fluid which, thanks in particular to the external fins, will exchange its heat. with the air flow on the one hand and the water spray on the other. In continuous operation, the temperature of the sprayed water is established at a value which is between the temperature of the primary flow and the temperature of the air.
  • the inlet temperature of the primary flow must be less than 100 ° C, while the outlet temperature of the same primary flow can at least be equal to the wet air inlet temperature more than 3 ° C.
  • the quantity of air required to carry out the above-mentioned cooling and / or condensation is calculated as a function of the power to be dissipated and of the inlet and outlet temperatures of the primary flow. Thanks to the device of the invention, it was possible to work with air speeds in the front section of the exchanger 7 between 3.0 and 4.5 m / s. This air speed corresponds to pressure drops of the order of 30 to 50mm of total pressure water column, which allows the use of a helical fan. In case the total fan pressure should be higher, it would be possible to use a centrifugal fan.
  • the amount of spray water is a function of the total area of the external fins 9 and of the pitch, that is to say of the interval separating two successive fins. It also depends on the thickness of the water film which is desired. Under normal spraying conditions, the applicant has found that the amount of spray water must be between 0.8 and 2.6m 3 / hm 2 of exchanger front section. In the case where the sprinkler system does not use carrier fluid, in particular compressed air, the water pressure at the spray nozzles 12 is between 0.5 and 7 bars.
  • the speed of the brine inside the exchanger was 2m / s for a total flow of 100m 3 / h.
  • the cooling air flow rate was 19.2 m 3 / s, the air entering at a temperature of 22.2 ° C and leaving at a temperature of 27.6 ° C.
  • the relative air humidity was 90%; at the exit of the exchanger it was 95%.
  • the front air passage section of the exchanger was 4.75m 2 .
  • the flow rate of the sprayed water was 10m 3 / h with a consumption of 590kg / h.
  • the installed power of two groups of axial fans was 15kW /.
  • tubes 8 provided with internal fins, making it possible to significantly improve the exchange. These were tubes with an outside diameter between 6 and 25mm, with fins of small height, ranging from 0.2 to 0.3mm, helically at 20 °, taken in the mass during the stretching of the tube . With this configuration, the ratio between the external exchange surface and the internal exchange surface was 7.3.
  • the exchanger included 160 tubes 8 distributed in eight rows, slightly offset with respect to each other, so that the tubes 8 are arranged at an equilateral triangular pitch.
  • Each transverse fin 9 is a rectangular plate of width l and height h .
  • the inclination of angle ⁇ of the exchanger 7 is chosen so that the diagonal 16 passing through the vertices 17, 18 respectively the highest and the lowest of each fin 9 has a substantially vertical direction.
  • the angle ⁇ is of the order of 22 °. If we take into account the usual values of l and h in exchangers whose tubes are provided with transverse fins, the angle ⁇ is between 5 and 35 °. As can be seen on examining FIG.
  • this particular arrangement by leading to an equal distribution of the tubes on either side of the diagonal 17, reduces the risks of water accumulation on the tubes located in the lower part of the exchanger.
  • This risk is further reduced by implementing spraying conditions which limit the thickness of the film over the entire exchange surface, while maintaining its continuous nature, namely by spraying drops of small dimensions, less than 120 micrometers per example of 60 to 120 micrometers, knowing that the conventional spray nozzles project drops of the order of 300 micrometers. Thanks to the better wettability of small drops, the projected water density could be lowered between 0.5 and 1m 3 / hm 2 of exchanger front section.
  • the internal means for intensifying the exchange can also consist of attached fins, in particular with helical ribbon or possibly wicks of different shapes, for example longitudinal linear fibers held against the internal surface of the tube by elastic threads. in a spiral, for example randomly interlaced wicks, for example wicks made of a metallic fabric, the chain of which is arranged longitudinally with respect to the general direction of the tube.
  • the external fins can be flat or spiral, crimped or brazed, or possibly taken in the mass or any other device intended to externally increase the exchange surface.
  • the device can operate with drawn air, as is the case in the example illustrated, or even with pushed air.
  • the circulation of the primary fluid inside the tubes of the exchanger is ensured by means of distribution boxes fitted with pipes or else by means of elbows and manifolds fitted with pipes.
  • the primary fluid inlet can be located in the upper part of the exchanger when it is a question of condensing a vapor or in the lower part of the exchanger when it is a question of cooling a fluid.

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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)
EP96490012A 1995-02-24 1996-02-23 Vorrichtung zum Kühlen einer Flüssigkeit oder Kondensieren von Dampf Withdrawn EP0730131A1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP96490012A EP0730131A1 (de) 1995-02-24 1996-02-23 Vorrichtung zum Kühlen einer Flüssigkeit oder Kondensieren von Dampf

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP95490007 1995-02-24
EP95490007 1995-02-24
EP96490012A EP0730131A1 (de) 1995-02-24 1996-02-23 Vorrichtung zum Kühlen einer Flüssigkeit oder Kondensieren von Dampf

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EP0730131A1 true EP0730131A1 (de) 1996-09-04

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EP96490012A Withdrawn EP0730131A1 (de) 1995-02-24 1996-02-23 Vorrichtung zum Kühlen einer Flüssigkeit oder Kondensieren von Dampf

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1698847A1 (de) * 2005-02-07 2006-09-06 Dambassinas Hippocrates Hybrides adiabatisches Wärmeaustauschsystem
WO2009077225A1 (de) * 2007-12-18 2009-06-25 A-Heat Allied Heat Exchange Technology Ag Modulares wärmeaustauschsystem
WO2010040635A1 (de) * 2008-10-08 2010-04-15 A-Heat Allied Heat Exchange Technology Ag Wärmetauscheranordnung und verfahren zum betrieb derselben
CN101903734B (zh) * 2007-12-18 2012-12-12 联合热交换技术股份公司 热交换系统
FR3006043A1 (fr) * 2013-05-27 2014-11-28 Gea Erge Spirale & Soramat Unite de refroidissement et procede de refroidissement
CN110986630A (zh) * 2019-12-18 2020-04-10 河钢股份有限公司 一种斜向空冷管束逆气流移动水膜布置系统
CN116007424A (zh) * 2022-12-29 2023-04-25 深圳市英维克科技股份有限公司 换热装置及空调设备
CN116147379A (zh) * 2022-12-29 2023-05-23 西麦柯(广东)制冷科技股份有限公司 一种冷凝器
CN119826573A (zh) * 2025-03-17 2025-04-15 安徽挪兰科技有限公司 一种一体式蒸发冷却冷水机组

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2278242A (en) * 1940-12-28 1942-03-31 Gen Electric Evaporative cooler
FR1509810A (fr) * 1966-02-03 1968-01-12 Du Pont échangeur de chaleur
FR2096556A1 (de) * 1970-06-29 1972-02-18 Baltimore Aircoil Co Inc
DE2250794A1 (de) * 1971-10-25 1973-05-03 Energiagazdalkodasi Intezet Kondensationseinrichtung fuer dampfturbinenkraftwerke
WO1990015299A1 (de) * 1989-05-30 1990-12-13 Jäggi Ag Bern Kühlanlage des hybriden typs

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2278242A (en) * 1940-12-28 1942-03-31 Gen Electric Evaporative cooler
FR1509810A (fr) * 1966-02-03 1968-01-12 Du Pont échangeur de chaleur
FR2096556A1 (de) * 1970-06-29 1972-02-18 Baltimore Aircoil Co Inc
DE2250794A1 (de) * 1971-10-25 1973-05-03 Energiagazdalkodasi Intezet Kondensationseinrichtung fuer dampfturbinenkraftwerke
WO1990015299A1 (de) * 1989-05-30 1990-12-13 Jäggi Ag Bern Kühlanlage des hybriden typs

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 8, no. 210 (M - 328)<1647> 26 September 1984 (1984-09-26) *

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1698847A1 (de) * 2005-02-07 2006-09-06 Dambassinas Hippocrates Hybrides adiabatisches Wärmeaustauschsystem
WO2009077225A1 (de) * 2007-12-18 2009-06-25 A-Heat Allied Heat Exchange Technology Ag Modulares wärmeaustauschsystem
CN101903734B (zh) * 2007-12-18 2012-12-12 联合热交换技术股份公司 热交换系统
WO2010040635A1 (de) * 2008-10-08 2010-04-15 A-Heat Allied Heat Exchange Technology Ag Wärmetauscheranordnung und verfahren zum betrieb derselben
AU2009301278B2 (en) * 2008-10-08 2015-11-19 A-Heat Allied Heat Exchange Technology Ag Heat exchanger assembly and method for the operation thereof
FR3006043A1 (fr) * 2013-05-27 2014-11-28 Gea Erge Spirale & Soramat Unite de refroidissement et procede de refroidissement
EP2808637A1 (de) * 2013-05-27 2014-12-03 GEA Ergé-Spirale et Soramat, S.A Kühleinheit und Kühlverfahren
CN110986630A (zh) * 2019-12-18 2020-04-10 河钢股份有限公司 一种斜向空冷管束逆气流移动水膜布置系统
CN116007424A (zh) * 2022-12-29 2023-04-25 深圳市英维克科技股份有限公司 换热装置及空调设备
CN116147379A (zh) * 2022-12-29 2023-05-23 西麦柯(广东)制冷科技股份有限公司 一种冷凝器
CN116147379B (zh) * 2022-12-29 2023-09-26 西麦柯(广东)制冷科技股份有限公司 一种冷凝器
CN119826573A (zh) * 2025-03-17 2025-04-15 安徽挪兰科技有限公司 一种一体式蒸发冷却冷水机组

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