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EP2397805B1 - Dispositif de refroidissement pour thermophores et composés de l'industrie du froid et pour refroidir les liquides ainsi que pour la récupération du froid en aération - Google Patents

Dispositif de refroidissement pour thermophores et composés de l'industrie du froid et pour refroidir les liquides ainsi que pour la récupération du froid en aération Download PDF

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Publication number
EP2397805B1
EP2397805B1 EP11004985.5A EP11004985A EP2397805B1 EP 2397805 B1 EP2397805 B1 EP 2397805B1 EP 11004985 A EP11004985 A EP 11004985A EP 2397805 B1 EP2397805 B1 EP 2397805B1
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EP
European Patent Office
Prior art keywords
heat exchanger
heat
cooling
air
air volume
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Application number
EP11004985.5A
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German (de)
English (en)
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EP2397805A3 (fr
EP2397805A2 (fr
Inventor
Heinz-Dieter Hombücher
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    • 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
    • F28C—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA COME INTO DIRECT CONTACT WITHOUT CHEMICAL INTERACTION
    • F28C3/00—Other direct-contact heat-exchange apparatus
    • F28C3/06—Other direct-contact heat-exchange apparatus the heat-exchange media being a liquid and a gas or vapour
    • F28C3/08—Other direct-contact heat-exchange apparatus the heat-exchange media being a liquid and a gas or vapour with change of state, e.g. absorption, evaporation, condensation

Definitions

  • the invention relates to a method for reducing the air volume flow in the recooling of heat transfer fluids and working fluids from refrigeration and liquid cooling and cooling recovery in ventilation technology from an air stream according to claim 1 and a device with a plurality of air streams, which are combined to form an air stream according to claim 2.
  • DE 202 21 407 U1 (also DE 101 40 279 A1 ) describes a device for the recooling of coolants or recooling media or for cooling.
  • DE 202 21 407 U discloses a method and an apparatus according to the preamble of claim 1 and claim 2.
  • the known recooling devices such as a cooling tower, hybrid cooler or dry cooler, are as well single-stage as a device according to DE 202 21 407 U1 is constructed.
  • the said recooling devices require a large airflow. For this reason, in the device according to DE 202 21 407 U1 the air flow is supersaturated with aerosols, which then change the physical state in the heat exchanger and evaporate under heat extraction, which can lead to a reduction of the air volume flow.
  • the water absorption of the air is limited by its saturation state.
  • the surface of the heat exchanger can not be wetted with water.
  • it is not usable for the evaporation of water.
  • a division or an adjustment of the recooling of the individual heat exchanger by admixture of at least one air flow is not possible.
  • the object of the invention is to cool the air flow as far as possible by evaporative cooling before entering the first heat exchanger and cool the air again by evaporative cooling before entering the at least one other heat exchanger and the heat exchanger surface also during the further course of the re-cooling of heat transfer and working fluids from refrigeration by moistening the heat exchanger surface for the energy extraction to use.
  • the object is achieved in a method according to the features of claim 1 and in a device according to the features of claim 2.
  • the recooling of heat transfer fluids and agents with a multi-stage process of humidification and wetting the heat exchanger surface with water, by the air is cooled by evaporative cooling before entering the first heat exchanger, then the air is reheated by at least one other heat exchanger and then removes the heat exchanger surface by wetting with water also the heat carrier or the working fluid further energy. It is particularly advantageous if the air from the first heat exchanger is heated so far that the air temperature after the first heat exchanger is higher than the air intake temperature of the first Heilbefeuchtungs thanks.
  • the heat transfer medium enters the recooling device when the last heat exchanger in the direction of air flow a, then flows through each further series-connected heat exchanger and leaves the recooling device at the air inlet of the first heat exchanger.
  • the invention is designed in a preferred construction by a series of heat exchangers and humidifiers in an air flow which is passed through a channel.
  • a series of heat exchangers and humidifiers in an air flow which is passed through a channel.
  • one or more air flow rates can be mixed in a preferred manner.
  • FIG. 1 the preferred arrangement with two humidifiers 1 and 3, two heat exchangers 2 and 5 and a wetting device 4 is shown.
  • FIG. 2 the preferred arrangement is shown with two humidifiers 1 and 3, two heat exchangers 2 and 5, a wetting device 4 and a connecting pipe 6 between the heat exchangers 2 and 5 in a countercurrent circuit.
  • FIG. 3 the preferred arrangement with two humidifiers 1 and 3, two heat exchangers 2 and 5 two wetting devices 4 and 9 is shown.
  • FIG. 4 the preferred arrangement is shown with three humidifiers 1, 3 and 7, three heat exchangers 2, 5 and 8, two wetting devices 4 and 9 and a connecting pipe 6 between the heat exchangers 2 and 5 in a countercurrent circuit.
  • FIG. 5 the preferred arrangement is shown with two humidifiers 1 and 3, two heat exchangers 2 and 5, two wetting devices 4 and 9 and a connecting pipe 6 between the heat exchangers 2 and 5 in a countercurrent circuit.
  • This arrangement is designed for the operation of a liquid chiller with free cooling.
  • the heat carrier (Fluid1) flows through the heat exchanger 5, the pipe 6, a valve 13, the heat exchanger 2 and a valve 12 to dissipate the condensation energy at warm Beeransaugtemperaturen a valve 10, a valve 11 and a valve 15 are closed here.
  • the heat transfer medium to be cooled (fluid 2) flows through a valve 14 is cooled by the liquid cooler and exits via a pipe 16 again.
  • the fluid 2 is pre-cooled with the heat exchanger 2, the so-called free cooling takes place.
  • the valves 14, 13 and 12 are closed and valves 11 and 15 are opened.
  • the condensation energy is removed via the heat exchanger 5 by the valve 10 is opened.
  • the course is flattened from point 4 to point 5 and shifted to higher humidity values of the air at low temperature.
  • This directly affects a reduction of the required air volume flow.
  • FIG. 8 For example, the preferred arrangement with two humidifiers 1 and 3, two heat exchangers 2 and 5, two humidifiers 4 and 9 and the piping 6 connecting the devices between the heat exchangers 2 and 5 are shown in parallel operation in a circuit.
  • This arrangement is designed for the operation of a liquid chiller for high energy output to the air flow.
  • the heat exchanger 2 the air is heated, so that they can absorb more water after the heat exchanger 2 by means of the humidifier 3 again.
  • the heat transfer in the following stage is, as before, improved by the wetting device 1 on the heat exchanger 2 in turn by the wetting device 3 on the heat exchanger 5.
  • FIG. 9 a closed cooling tower 18 is shown, which has a cooling water device 19, an air supply 20, which generates a cooling air flow K, and a standard heat exchanger 21.
  • the cooling water device 19 is provided as standard with a fresh water supply, an overflow and a discharge device.
  • the standard heat exchanger 20 is preferably sprinkled by means of a sprinkler 22 with supplied or separated from the cooling air flow K water and thus recovers the energy from the heat transfer or working fluid from the refrigeration for the cooling tower 18 to be cooled plant 24.
  • the heat carrier is in a closed heat transfer circuit 23 and is provided with a corresponding pump and control 25.
  • an additional heat exchanger 2 is arranged above the sprinkler 22 (also in FIG FIG. 4 shown as heat exchanger 2).
  • a moistening device 3 and, according to the invention, a further heat exchanger 5 (also in FIG FIG. 4 shown as heat exchanger 5).
  • the heat exchanger 2 is connected by means of a pipe 26 and a three-way valve 28 to the heat transfer circuit 23 of the cooling tower 18.
  • the heat exchanger 5 is connected by means of a pipe 27 and a three-way valve 29 to the heat transfer circuit 23 of the cooling tower 18.
  • the moistening device 3 is connected by means of a pipe 30 to a water outlet of the cooling water device 19 and is thus supplied with existing already in the system moistening water.
  • the cooling tower 18 can be better utilized. Either higher power can be guaranteed. Furthermore, the cooling tower can be made smaller. But above all, the power consumption of the air supply 20 can be significantly reduced, since by means of the additional heat exchanger 2, 5 in the leadership of the cooling air flow significantly improved cooling of the heat carrier succeeds.

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

Claims (14)

  1. Méthode pour la réduction du flux volumique d'air au refroidissement des caloporteurs et des agents du refroidissement, avec au moins un conduit d'air, au moins un échangeur de chaleur (2) et un humidificateur placé en avant (1), à condition que l'humidificateur (1) produit un aérosol au flux volumique d'air avant l'échangeur de chaleur an aval (2) qui évapore au flux volumique d'air, caractérisée par
    que le flux volumique d'air qui sort de l'échangeur de chaleur (2) est humidifié encore une fois et est dirigé au moins à un autre échangeur de chaleur (5) et que, pour l'augmentation l'effet de refroidissement, une humidification directe de la surface d'autre échangeur de chaleur (2, 5) a lieu à l'aide d'un dispositif de mouillage (4, 9) au moins et que l'évaporation du mouillage de la surface se fait dans l'autre 'échangeur de chaleur (2, 5) et que l'humidité est transportée de l'autre échangeur de chaleur (2,5) par un flux volumique d'air.
  2. Dispositif pour la réalisation d'une méthode selon la revendication 1 avec au moins un conduit d'air, un échangeur de chaleur (2) et un humidificateur (1) qui est avent l'échangeur de chaleur, de telle sorte que l'humidificateur (1) produit un aérosol au flux volumique d'air avent l'échangeur de chaleur en aval qui évapore au flux volumique d'air,
    caractérisé par qu' au moins un deuxième échangeur de chaleur (5) est situé après un premier échangeur de chaleur (2) dans le canal d'air et qu'au moins un humidificateur (3) est situé après le premier échangeur de chaleur (2) pour le refroidissement par évaporation et qu'au moins un dispositif (4) pour le mouillage direct de la surface du deuxième échangeur de chaleur (5) en aval est situé après l'humidificateur.
  3. Dispositif selon la revendication 2 avec un dispositif (17) pour l'addition au moins d'un flux volumique d'air dans le conduit d'air au plus tôt après le premier échangeur de chaleur (2) pour régler la puissance de l'échangeur de chaleur suivant (5).
  4. Dispositif selon les revendications de 1 à 3 pour le couplage en parallèle de l'échangeur de chaleur (2, 5), ainsi que l'énergie de condensation d'une machine de réfrigération est au moins distribué de manière uniforme ou réglé en deux échangeurs de chaleur (2, 5) au flux volumique d'air.
  5. Dispositif selon les revendications 2 ou 3 avec une installation (6) pour le couplage du débit de caloporteur selon le principe du contre-courant par deux échangeurs de chaleur (5, 2) au moins.
  6. Dispositif selon les revendications de 2 à 5 avec une installation (6) pour le couplage du débit de caloporteur selon le principe du contre-courant par des échangeurs de chaleur en quantité ad libitum.
  7. Dispositif selon les revendications de 2 à 6 avec une installation (6, 16) pour le couplage du débit de caloporteur pour un débit d'écoulement tour à tour des échangeurs de chaleur (2, 5) pour la dissipation de l'énergie de condensation d'une refroidisseur de liquides ou pour l'écoulement des échangeurs de chaleur (2, 5) pour le caloporteur à refroidir de refroidisseur de liquides.
  8. Dispositif selon les revendications de 2 à 7 avec une installation (6, 16) pour le couplage du débit de caloporteur pour un débit d'écoulement tour à tour des échangeurs de chaleur (2, 5) pour la dissipation de l'énergie de condensation d'une refroidisseur de liquides ou pour l'écoulement des échangeurs de chaleur (2, 5) pour le caloporteur d'un rétablissement de chaleur.
  9. Dispositif selon les revendications 7 ou 8 avec une installation pour le couplage du débit de caloporteur par des vannes trois voies (de 10 à 15).
  10. Dispositif selon les revendications de 2 à 9 avec des installations d'humidification d'air (8, 1, 3) pour le refroidissement par évaporation.
  11. Dispositif selon les revendications de 2 à 9 avec des installations de mouillage tour à tour (9, 4) pour la surface de l'échangeur de chaleur (2, 5).
  12. Dispositif selon les revendications de 1 à 3 pour le couplage parallèle de l'échangeur de chaleur de sorte que l'énergie de condensation d'une machine frigorifique est distribué uniformément ou réglé sur deux échangeurs de chaleur au flux volumique d'air au moins.
  13. Dispositif selon les revendications de 1 à 11 dans une tour refroidissement à circuit fermée avec une alimentation en air de refroidissement, un système d'arrosage, avec un échangeur de chaleur en standard avec un circuit fermé et avec un échangeur de chaleur au moins (3, 4, 5) et un humidificateur en amont après l'échangeur de chaleur en standard de la tour réfrigération à circuit fermée.
  14. Dispositif selon les revendications de 1 à 11 dans une tour refroidissement hybride, qui est une tour refroidissement à circuit fermée, avec une alimentation en air de refroidissement, un système d'arrosage, avec un échangeur de chaleur en standard avec une installation de mouillage ainsi qu'avec un circuit fermé et avec un échangeur de chaleur (3, 4, 5) au moins et un humidificateur en amont après l'échangeur de chaleur en standard de la tour réfrigération à circuit fermée.
EP11004985.5A 2010-06-18 2011-06-18 Dispositif de refroidissement pour thermophores et composés de l'industrie du froid et pour refroidir les liquides ainsi que pour la récupération du froid en aération Active EP2397805B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010024281 2010-06-18
DE201110103625 DE102011103625A1 (de) 2010-06-18 2011-06-08 Vorrichtung zur Rückkühlung von Wärmeträgern und Arbeitsstoffen aus der Kältetechnik und Flüssigkeitskühlern sowie Kälterückgewinnung in der Lüftungstechnik

Publications (3)

Publication Number Publication Date
EP2397805A2 EP2397805A2 (fr) 2011-12-21
EP2397805A3 EP2397805A3 (fr) 2014-07-16
EP2397805B1 true EP2397805B1 (fr) 2017-09-06

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Application Number Title Priority Date Filing Date
EP11004985.5A Active EP2397805B1 (fr) 2010-06-18 2011-06-18 Dispositif de refroidissement pour thermophores et composés de l'industrie du froid et pour refroidir les liquides ainsi que pour la récupération du froid en aération

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EP (1) EP2397805B1 (fr)
DE (1) DE102011103625A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2986858B1 (fr) * 2012-02-13 2014-03-07 Edouard Serras Procede et dispositif de regulation de la temperature et de l'humidite relative dans un batiment
PL3143358T3 (pl) 2014-05-15 2021-08-02 Frigel Firenze S.P.A. Mieszany konwektor
CN108800984B (zh) * 2018-08-09 2025-03-11 茌平信发聚氯乙烯有限公司 一种不易结垢的电石清液循环冷却装置及方法

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1051296B (de) * 1956-06-25 1959-02-26 Escher Wyss Gmbh Verdunstungskuehler
GB845844A (en) * 1959-02-11 1960-08-24 Gea Luftkuhler Gesselschaft M Evaporating cooling plant
US3659623A (en) * 1969-12-02 1972-05-02 Baltimore Aircoil Co Inc Water supply system
DE10140279A1 (de) 2001-08-16 2003-03-06 Ludwig Michelbach Vorrichtung und Verfahren zur Rückkühlung von Kühlmitteln oder Rückkühlmedien oder zur Kältegewinnung
DE10258066A1 (de) * 2002-12-11 2004-06-24 Thyssenkrupp Encoke Gmbh Koksofengaskühler
US20100032850A1 (en) * 2008-08-05 2010-02-11 Lin sui-ming De-Fouling Tubes for Cooling Tower

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DE102011103625A1 (de) 2012-06-14
EP2397805A3 (fr) 2014-07-16
EP2397805A2 (fr) 2011-12-21

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