DE102018201070A1 - Frischluftkonditioniervorrichtung and method for operating such a device - Google Patents

Abstract

It is a Frischluftkonditioniervorrichtung and methods for operating such a device, which are energy-saving compared to the prior art. For reasons of hygiene, in building air conditioning, a certain amount of room air is always replaced by outside air. This fresh air flow, called outside air for short, must be conditioned by ambient conditions to the room entry conditions. In this case, the thermodynamic potential difference (temperature and water content) between the building air to be replaced, called exhaust air for short, and the outside air is exploited first so that as little primary energy as possible for the change in state of the ambient air flow (outside air) to the room entry state (supply air) must be used ( Heat recovery or enthalpy recovery). The air conditioning device integrates the various process steps in one apparatus and makes it possible to cover the additionally required energy demand to be introduced into the process year-round, reliably and completely by means of low-temperature waste heat. So it can be completely dispensed with the use of conventional chillers in the summer, and the associated investment and operating costs.

Description

The invention relates to a Frischluftkonditioniervorrichtung according to claim 1 and method for operating such a device according to claim 3, 4, 6 or 8.

• • Sommer: Kühlen, und Entfeuchten
• • Winter: Erwärmen und Befeuchten

For reasons of hygiene, in building air conditioning, a certain amount of room air is always replaced by outside air. This fresh air flow, called outside air for short, must be conditioned by ambient conditions to the room entry conditions. In this case, the thermodynamic potential difference (temperature and water content) between the building air to be replaced, called exhaust air for short, and the outside air is exploited first so that as little primary energy as possible for the change in state of the ambient air flow (outside air) to the room entry state (supply air) must be used ( Heat recovery or enthalpy recovery). After this energy recovery step, the air additionally experiences the following summary state changes:

• • Summer: cooling and dehumidifying
• • Winter: heating and humidifying

The changes in the state of outdoor air in summer, cooling and dehumidifying, are achieved by the use of either electrically or thermally driven chillers. The pre-conditioned outside air on the cold surface of a heat exchanger cools down to temperatures around 10 ° C and the excess amount of water in the air condenses on the heat exchanger surfaces (below the dew point). Then the air has to be heated up again until it reaches the room inlet temperature. In winter, the air must be heated and humidified, that means the air is heated with a heat exchanger and then the hot air is humidified in an adiabatic evaporative cooler to room entry conditions and cooled.

Kondensator (Wärmetauscher)

: Entfeuchtung und Kühlung im Sommerbetrieb

Nacherhitzer (Wärmetauscher)

: Erwärmung in Sommer- und Winterbetrieb

Adiabatischer Verdampfer

: Befeuchtung im Winterbetrieb, Kühlung im Sommer

These processes take place in a ventilation device that contains the appropriate replacement devices for these state changes:

Condenser (heat exchanger)

: Dehumidification and cooling in summer operation

Reheater (heat exchanger)

: Warming in summer and winter operation

Adiabatic evaporator

: Humidification in winter operation, cooling in summer

Assuming that the outside air is not too humid, the room inlet temperature can also be effected by adiabatic evaporative cooling (for example Fa. Condair, Munters, etc.). However, as the cooling limit of the air in summer is sometimes well above 20 ° C, this technology can not guarantee the achievement of the required room inlet temperature during the entire cooling period and thus the chiller is additionally required. An improvement brings the use of indirect evaporative coolers (for example, the company Coolerado, Messrs. Kampmann, Oxycom, etc.)

This technology can reach significantly lower temperatures than the adiabatic evaporation technique, but fails at higher outdoor humidities and then requires the chiller for dehumidification.

Remedy is the use of sorption technology to dehumidify the air before the actual cooling. There are sorbent dehumidifiers with solid sorbents (sorbers) (Munters, Klingenburg) and liquid sorbents (L-DCS Technology, Germany; Advantix, USA, Menerga, Germany; AIL-Research, USA) ).

• • Entfeuchtung mit einem Sorptionsapparat
• • Befeuchtung mit einem direkten oder indirekten Verdunstungskühler

In any case, the process control looks like this:

• • Dehumidification with a sorption apparatus
• • Humidification with a direct or indirect evaporative cooler

The goal today is to fully and economically cover the drive energy for building air conditioning from low-temperature heat (district heating, geothermal energy) or existing waste heat (block heat and power plants, compressed air compressors, solar thermal energy, etc.). The drive energy is usually not available at the same time as the air conditioning requirement. A suitable technology must therefore not only be able to be driven completely with low-temperature heat (about 65-75 ° C), but must also be able to effectively store the drive energy, if possible without losses.

• Feste Sorptionstechnologie (Sorptionsräder)
  • • hoher Druckverlust beim Durchströmen mit Luft -> erhöhter Hilfsenergiebedarf
  • • hohe Regenerationstemperaturen → Antriebstemperaturen > 75°C
  • • Ungünstige Dimensionen → teurer Einbau
  • • Keine Energiespeicherung möglich
  • • adiabatischer Prozess benötigt Zwischenkühlung nach der Sorption → zusätzlicher Apparateaufwand
• Flüssige Sorptionstechnologie (offene Sorption)
  • • Nur in Verbindung mit gekühlter Prozessführung genügend leistungsfähig, Prozesskühlung benötigt zusätzliches Rückkühlwerk → zusätzliche Kosten
  • • Sorbensaustrag („carry over“) durch Abscheider verhindert-> erhöhter Hilfsenergiebedarf
• Außer L-DCS Technology:
  • • Keine Energiespeicherung Adiabatische Verdunstungskühlung
  • • direkte Befeuchtung der Luft -> geringes Kühlpotential
  • • keine Indirekte Verdunstungskühlung
  • • hoher Druckverlust beim Durchströmen mit Luft -> erhöhter Hilfsenergiebedarf Zusätzlich zu diesen Nachteilen müssen diese Technologien als eigene Apparate einzeln in das Lüftungsgerät integriert werden, was den Einbauaufwand erhöht und damit die Wettbewerbsfähigkeit reduziert.

The technologies in question have the following disadvantages, which make use under these conditions questionable:

• Fixed sorption technology (sorption wheels)
  • • high pressure loss when flowing through air -> increased auxiliary energy requirement
  • • high regeneration temperatures → drive temperatures> 75 ° C
  • • Unfavorable dimensions → expensive installation
  • • No energy storage possible
  • • Adiabatic process requires intermediate cooling after sorption → additional equipment
• Liquid sorption technology (open sorption)
  • • Only powerful enough in conjunction with cooled process control, process cooling requires additional recooling system → additional costs
  • • Sorbent discharge ("carry over") prevented by separators-> increased auxiliary energy requirement
• Except L-DCS Technology:
  • • No energy storage Adiabatic evaporative cooling
  • • Direct humidification of the air -> low cooling potential
  • • no indirect evaporative cooling
  • • high pressure loss when flowing through air -> increased auxiliary energy demand In addition to these disadvantages, these technologies must be integrated as separate devices in the ventilation unit, which increases the installation costs and thus reduces competitiveness.

It is therefore an object of the present invention to provide an air conditioning device and to provide methods for operating the device, which are energy-saving compared to the prior art.

The solution of this object is achieved by the features of claims 1, 3, 4, 5 and 7, respectively.

The Luftkonditioniervorrichtung according to claim 1 or 5 avoids these disadvantages, integrates the process steps in an apparatus and makes it possible to cover the additionally required, and introduced into the process, energy needs year-round, reliable and complete by low-temperature waste heat. So it can be completely dispensed with the use of conventional chillers in the summer, and the associated investment and operating costs.

• - der offenen Sorptionstechnologie,
• - der indirekten Verdunstungskühlung
• - der überwiegenden Gegenstromführung zwischen den gasförmigen Medien
• - der Energierückgewinnung
• - minimaler Hilfsenergiebedarf durch minimalen Druckverlust im kompakten Gerät folgende zusätzlicher Funktionen:
• - Energiespeicherung und
• - Energietransport ohne Verluste an Luftkonditionierungspotential.

The new air conditioning device offers due to integration of:

• - open sorption technology,
• - indirect evaporative cooling
• - The predominant countercurrent flow between the gaseous media
• - the energy recovery
• - minimal auxiliary power requirement due to minimal pressure loss in a compact device the following additional functions:
• - Energy storage and
• - Energy transport without loss of air conditioning potential.

The sorbent or the desiccant solution can be regenerated in a suitable regeneration apparatus of the company L-DCS Technology GmbH with low-temperature heat (eg geothermal energy, waste heat from: CHP, CO2 heat pumps, compressed air compressors etc), the water absorbed during the absorption being recovered is evaporated and the sorbent can be reused lossless. Through the use of very small quantity distributors according to the DE 10 2010 041 289 A1 it is possible dehumidification capacity, or thus by equipping the evaporative cooling process gleichzusetzende cooling capacity, on the storage of pure dehumidification capacity in the liquid sorbent itself to achieve cost and without loss of cooling capacity. As a result, not only the possibility of expensive drive energy by existing waste heat operating costs and replace without CO ₂ release, but also by lowering the evaporative cooling temperature and the reliable, year-round provision of cooling capacity to dispense with the installation of a redundant chiller by the new device. These savings, in conjunction with the simple, inexpensive to manufacture device give an extreme economic and technical advantage over the prior art.

• - Investitionskosten werden reduziert,
• - Betriebskosten werden reduziert,
• - Primärenergieeinsatz wird verringert,
• - Einsatz von potenziell Treibhauseffekt kritischen Substanzen wird vermieden.

Such a device is used primarily in the air conditioning of buildings. Overall, the following advantages result:

• - Investment costs are reduced,
• - operating costs are reduced,
• - Primary energy input is reduced,
• - Use of potentially greenhouse effect critical substances is avoided.

The dependent claims have advantageous embodiments of the invention the subject.

Further details, features and advantages of the invention will become apparent from the following description with reference to the drawing.

• 1 eine perspektivische Darstellung einer ersten Ausführungsform der Erfindung mit zwei Sektionen;
• 2 eine 1 entsprechend Darstellung mit transparenter Außenwand;
• 3 eine 1 entsprechend Darstellung mit Schnittebene A - A;
• 4a und 4b Schnittdarstellungen entlang Ebene A -A in 3 und entlang Ebene B - B in 4a;
• 5 ein Funktionsschaltbild der ersten Ausführungsform im Sommerbetrieb;
• 6a und 6b eine nur für den Sommerbetrieb geeignete Variante der ersten Ausführungsform;
• 7 ein Funktionsschaltbild der ersten Ausführungsform in einem alternativen Sommerbetrieb;
• 8 eine perspektivische Darstellung einer zweiten Ausführungsform der Erfindung mit drei Sektionen;
• 9a und 9b Schnittdarstellungen der zweiten Ausführungsform entsprechend 4a und 4b im Sommerbetrieb;
• 10 einen alternativen Sommerbetrieb der zweiten Ausführungsform;
• 11 eine weitere Variante eines Sommerbetriebs;
• 12 eine Darstellung eines Winterbetriebs der zweiten Ausführungsform; und
• 13a und 13b einen alternativen Winterbetrieb.

It shows

• 1 a perspective view of a first embodiment of the invention with two sections;
• 2 a 1 as shown with transparent outer wall;
• 3 a 1 as shown in section A - A;
• 4a and 4b Sectional views along plane A -A in 3 and along level B - B in 4a ;
• 5 a functional diagram of the first embodiment in summer mode;
• 6a and 6b a suitable only for summer operation variant of the first embodiment;
• 7 a functional diagram of the first embodiment in an alternative summer operation;
• 8th a perspective view of a second embodiment of the invention with three sections;
• 9a and 9b Sectional views of the second embodiment accordingly 4a and 4b in summer operation;
• 10 an alternative summer operation of the second embodiment;
• 11 another variant of a summer operation;
• 12 a representation of a winter operation of the second embodiment; and
• 13a and 13b an alternative winter operation.

The 1 to 7 show a first embodiment of the invention with a material and heat exchange reactor 2 containing a plurality of mass and heat exchange surfaces 4 on opposite sides of a plurality of liquid-impermeable heat transfer plates 6 are formed. Between the heat transfer plates 6 are alternating primary air channels 8th and secondary air ducts 10 educated. The primary air channels 8th run between a primary air inlet 12 and a primary air outlet 13 for primary air in the form of fresh air. The secondary air channels 10 run between a secondary air inlet 14 and a secondary air outlet 15 , Primary air and secondary air are essentially fed in countercurrent. In order to avoid mixing in the supply and discharge of primary and secondary air, the secondary air entrances are 14 and the secondary air outlets 15 in 1 and 2 at the top and bottom of the material and heat exchanger 2 provided while the primary air entrances 12 and the primary air outlets 13 at the back and front of the fabric and heat exchanger 2 are provided.

The mass and heat exchange reactor 2 is a first 16 and second section 18 split, with the first section 16 in the flow direction of the primary air before the second section 18 is arranged. A first liquid distributor 20 is in the first section 16 and a second liquid distributor 22 is in the second section 18 arranged. The first liquid distributor 20 is solely for forming a liquid film on the fabric and heat exchange surfaces 4 in the first section 16 educated. The second liquid distributor 22 is for the formation of a thin, closed liquid film on one or both fabric and heat exchange surfaces 4 the heat transfer plates 6 in the second section 18 designed. It may be both a water film and a thin liquid film of desiccant solution or sorbent. Under the primary air channels 8th and under the two liquid distributors 20 . 22 are associated first and second liquid collector 24 , 25 provided.

3 shows one 2 corresponding representation with a sectional plane A from which is the sectional view in 4a results. 4b shows a sectional view taken along the line B - B in 4a , The in the 4a . 4b and 1 - 3 shown material and heat exchanger 2 do not correspond completely, since in the representations after 1 - 3 the outermost channels primary air channels 8th are while in the 4a and 4b the outermost channels secondary air channels 10 are. 4a and 4b represent the preferred summer mode. 6a and 6b show a special embodiment of the Soff- and heat exchanger 2 for the summer operation. 5 represents an alternative method for summer operation. 7 serves to explain the winter operation.

The material and heat exchanger 2 It is designed in such a way that the liquid flows do not mix and the air streams do not mix uncontrollably. In the embodiment according to 1 to 7 are alternating side by side primary air ducts 8th and secondary air ducts 10 intended. In the primary air channels 8th the primary air flow is thus guided to be conditioned airflow. The secondary air flow in the secondary air ducts essentially serves to cool the primary air flow by evaporating water. The secondary air flow is conducted in countercurrent to the primary air flow.

The material and heat exchanger 2 to 1 to 7 included the first section 16 and the second section 18 which are arranged one behind the other in the flow direction. The main task of the second section 18 consists in setting the desired primary humidity. In the second section 18 the primary air flow is humidified or dehumidified by contact with a suitable liquid sorbent (depending on the concentration of incoming sorbent and the temperature of primary air flow and secondary air flow). These are the fabric and heat exchange surface 4 the second section 16 on the primary side with a thin sorbent film, and on the secondary side with a water film, wetted. To support the generation and maintenance of these thin films are the fabric and heat exchange surface 4 each covered with a wetting acting surface structure. The liquids are from small quantity distributors 20 . 22 located above the fabric and heat exchange surface 4 are arranged on the fabric and heat exchange surfaces 4 abandoned, run down on you and become, by means of below the material and heat exchange surface 4 arranged liquid collector 24 . 26 completely absorbed and derived. At the end at which the primary air enters the second section 18, the secondary air exits the secondary region of the air conditioning device laterally to its flow direction upwards and / or downwards through suitable openings 14 . 15 like this from the 1 . 2 as well as 4, 5 and 7 can be seen.

The main task of the first section 16 consists in the cooling of the primary air flow without humidity change. In the first section 16 the primary air flow is through a heat-transferring exchange wall 6 with the secondary air flow in connection. In this case, the secondary area of the exchange surface 4 (Which is exposed to the secondary air flow), according to the execution of the secondary region of the second section 18 , also through a micro liquid distributor 22 Impounded with water, which runs down, which also provided with a wetting-acting surface structure, surface, and also from a, arranged below the exchange surface, liquid collector 26 is caught and discharged. The water-moist surface 4 is in direct contact with the secondary air flow. The heat required for the onset of evaporation of the water from the water film in the secondary air flow is largely the primary air flow through heat conduction through the exchange wall 6 withdrawn. In this case, the primary air flow cools down and the secondary air flow heats up. By appropriate air flow in summer, the secondary air flow from a partial air flow of the primary air flow is formed, typically about 25% -50%. As a result, due to the thermodynamically optimal cooling potential, the lowest temperatures in the primary air flow can be achieved, which can be achieved by indirect evaporative cooling in the secondary air flow, definitely well below the temperatures that are possible when using the building exhaust air as a secondary air flow. In cases where no, or only little, cooling of the primary air flow is needed, building air is used as secondary air. In this case, the cooling effect is less effective. When switching off the liquid supply, the first section works 16 as pure heat recovery (winter operation).

Summer operation with exhaust air - Fig. 4a and 4b

The use of exhaust air as secondary air means that the cooling potential of the indirect evaporative cooling in the first section 16 is limited by the cooling limit temperature of the room exhaust air. This means that the lowest temperature to be reached in the primary air flow is actually limited to approximately 20-22 ° C. If a partial air flow of the primary air flow is used as a secondary air flow, this limit drops from the room air cooling limit in the direction of the dew point of the primary air, depending on how much air is diverted. If ideally branched off at about 25% -50%, realistic primary air temperatures of less than 16 ° C can be achieved, which is more than sufficient for building air conditioning.

If the humidity of the primary air is higher than the desired room air content or if the primary air temperatures rise at the outlet of the first section 16 above the desired temperature, you can see the primary air in the second section 18 before entering the first section 16 dehumidify and so the real achievable cooling temperatures of the first section 16 Reliably lower and at the same time keep the moisture limits. All these functions are operated by one and the same apparatus, without the need to use further exchange apparatus, which cause further costs, further pressure loss and further size or additional weight.

If the primary air has a high temperature but a low humidity, you can also see the brine mass flow of the second section 18 turn off completely and the second section 18 with it, as well as the first section 16 , as a pure indirect evaporative cooler use. This effectively doubles the effective exchange area for the evaporative cooling process, greatly increasing the level of exchange of the evaporative cooling process - just what you need at very high temperatures.

Alternative summer mode - Fig. 5

• - konsequenten Gegenstrom von Primär- und Sekundärluftstrom
• - ohne die Wärme zunächst auf ein weiteres Kühlmedium (Kühlwasser), und dann noch einmal auf ein Rückkühlwerk zu übertragen (weniger Verluste...).
• - Integration von Entfeuchter und indirektem Kühler in einen Apparat. Das bedeutet die Luftströme werden beim Übergang von einem Verfahrensschritt zum nächsten nicht durch umleiten, trennen oder sonst wie mit zusätzlichen Druckverlusten beaufschlagt, die zu einer Erhöhung des Hilfsenergiebedarfs führen (Lüfterleistung).

In summer mode, the goal is to reliably cool the primary air to the room inlet temperature and to dehumidify it to the room humidity. The cooling of the primary air becomes essential in the first section 16 by humidifying the secondary air, eg exhaust air from the building, achieved. One avoids it on the one hand for reasons of hygiene, and on the other hand, to maintain the correct humidity, to bring the primary air directly into contact with water. In order for the air to have the right humidity, it first enters the second section 16 dehumidified by contact with the concentrated brine film. The released heat is through the exchange wall 6 the second section 18 also transferred to the secondary air. The heat is thereby directly into the water film of the second section 18 transferred, and converted directly into evaporative cooling. This is done in a thermodynamically ideal way by:

• - Consistent counterflow of primary and secondary air flow
• - without first transferring the heat to another cooling medium (cooling water), and then again to a recooling unit (fewer losses ...).
• - Integration of dehumidifier and indirect cooler in an apparatus. This means that during the transition from one process step to the next, the air streams are not diverted, separated or otherwise subjected to additional pressure losses, which lead to an increase in the auxiliary energy requirement (fan power).

In many countries, only the summer operation, ie the air conditioning of indoor air is in demand 6a and 6b an embodiment of the material and heat exchanger 2 specified, which is only suitable for summer operation. How out 4a . 4b and 5 can be seen in the first section 16 the mass transfer surfaces 4 not required. Therefore, in the embodiment according to 6a and 6b in the first section 16 with a plurality of stacked rectangular flow channels 28 Mistake. This will increase the stability of the material and heat exchanger 2 elevated.

Winter operation - Fig. 7

• - Temperatur des Wassers auf 70°C anheben (tötet z. B. Legionellen auf der Fläche und vor allem in den Flüssigkeitsverteilern ab)
• - Vollentsalztes Wasser aus einer Umkehrosmoseanlage verwenden, das:
  • - keine Bakterien enthält
  • - das Bilden von Ablagerungen in dem Apparat verhindert
• - Nur genau die benötigte Wassermenge auf der Fläche aufbringen, die dann auch vollständig verdunstet, was durch den Kleinstmengenverteiler einfach möglich ist.
• - regelmäßig die ganze Fläche vollständig abtrocknen lassen (täglich ca. 1h) dadurch wird die Fläche frei von Bakterien und Algen gehalten, die nur in wässeriger Umgebung existieren kann.

In winter operation, the primary air is conditioned as much as possible to the exact room entry condition. The air is heated and moistened. This is achieved by using a diluted, preheated (about 50 ° C) brine film in the second section 18 is applied to the exchange surface and comes into contact with the primary air. Due to the high temperature, water should be evaporated from the brine into the primary air. The secondary air channels 10 are not used in winter operation. Thus, all heat energy in the liquid films of the first and second sections 16 . 18 concentrated only on the humidification and heating of the primary air flow. Theoretically, one could also in winter operation, the brine in section 2 replaced by water and thereby achieve an increase in evaporation performance. But then you have a direct contact of the primary air (supply air) with warm water, which may meet with users for reasons of hygiene may refuse. Against the hygiene problems one can take the following measures:

• - raise the temperature of the water to 70 ° C (kills, for example, legionella on the surface and especially in the liquid distributors)
• - Use demineralized water from a reverse osmosis system, which:
  • - contains no bacteria
  • - prevents the formation of deposits in the apparatus
• - Only apply exactly the required amount of water on the surface, which then evaporates completely, which is easily possible due to the small quantity distributor.
• - regularly allow the whole area to dry completely (daily approx. 1 hour), keeping the area free of bacteria and algae that can only exist in an aquatic environment.

Alternatively - not shown - you can go the opposite way and on the exchange surface 4 the first section 16 also use thin brine in place of water. In the thin hot brine no algae or bacteria can survive. Also in this way the hygiene discussion can be solved.

The 8th to 13b show a second embodiment of the invention, which differs from the first embodiment in that the substance and heat exchange 2 a third section 30 which, in the direction of flow of the primary air before the second section 18 is arranged. As in particular from the perspective view in 8th can be seen extends the third section 30 the flow channels 10 for primary air, so that the primary air inlet 12 in the third section 30 shifts. The primary air channels 10 in the third section 30 are each between tertiary flow channels 32 arranged and the primary air flow channels 10 of the third section 30 and the tertiary air flow channels 32 are by water vapor permeable, but not air permeable heat and pulp exchange structures 34 separated from each other. The tertiary air is supplied via upper and / or lower tertiary air entrances 36 and tertiary air outlets 38 the tertiary air channels 32 added and removed. The tertiary air inlet 36 into the third section 30 is near the end of the second section 18 , The tertiary air is thus introduced transversely to the primary air flow direction, but then to be guided in substantially countercurrent to the primary flow direction. The secondary air in the second section 18 is also discharged laterally or above and / or below.

• - be- oder entfeuchtet bzw.
• - erwärmt oder abgekühlt.

The main task of the third section 30 consists in the heat and material recovery in the primary air flow. In the third section 30 the primary air flow is through an airtight but water vapor and heat permeable membrane 34 with the tertiary air flow (exhaust air from the building) in exchange. In accordance with the thermodynamic gradient between primary air and tertiary air, the primary air flow thereby becomes from the tertiary air flow:

• - humidified or dehumidified or
• - heated or cooled.

9a and 9b show a den 4a and 4b corresponding summer operation of the material and heat exchanger 2 with three sections 16 . 18 and 30 , Due to the tertiary air flow in the tertiary air ducts 32 We additionally pre-cooled the primary air in the primary air ducts and, if necessary, pre-dehumidified.

The summer operation after 10 differs from the summer mode 9a and 9b in that in the second section 18 on the dehumidification of the primary air flow in the primary air ducts 8th is omitted with brine. There is only the pre-dehumidification and cooling in the third section 30 over the membrane 34 ,

The summer operation after 11 differs from the summer mode 9a and 9b only in that the primary air in the first section 16 is additionally moistened and cooled by a thin film of water.

12 shows a winter operation in which the primary air in the third section 30 is heated and moistened. In the second and first section 18 . 16 the primary air is further heated and in the first section 16 additionally moistened by a water film.

The winter operation after 13a and 13b differs from winter operation 12 in that in the second section 18 the primary air flow is additionally moistened by a strongly diluted liquid film of drying agent solution of the primary air flow. The heat for the evaporation of water from the desiccant film is through the secondary air flow in the second section 18 provided.

LIST OF REFERENCE NUMBERS

2

Material and heat exchanger

4

Fabric and heat exchange surfaces

6

Heat exchange plates

8th

Primary air channels

10

Secondary air ducts

12

Primary air inlet

13

Primary air output

14

Secondary air input

15

Secondary air outlet

16

first section of 2

18

second section of 2

20

first liquid distributor

22

second liquid distributor

24

first liquid collector

26

second liquid collector

28

rectangular flow channels

30

third section of 2

32

Tertiary air ducts

34

Membrane, heat and mass transfer structure

36

Tertiary air input

38

Tertiary air output

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102010041289 A1 [0015]

Claims (14)

Air conditioning device with a mass and heat exchange reactor (2) having a plurality of mass and heat exchange surfaces (4) formed on opposite sides of a plurality of liquid impermeable heat exchange plates (6); the air and liquid flow channels (8, 10, 32) limit, a primary air inlet (12) and a primary air outlet (13), between which primary air ducts (8) are formed, a secondary air inlet (14) and a secondary air outlet (15), between which secondary air ducts (10) are arranged, wherein between the heat transfer plates (6) alternately primary air ducts (8) and secondary air ducts (10) are formed, wherein the mass and heat exchange reactor (2) is divided into a first and a second section (16, 18), wherein the first section (16) is arranged upstream of the second section (18) in the direction of flow of the primary air, a first liquid distributor (20) in the first section (16) which is designed exclusively for wetting the material and heat exchange surfaces (4) with water, and a second liquid distributor (22) in the second section (18) for wetting the material and heat exchange surfaces (4) with water or desiccant solution, wherein the primary and secondary air passages (8, 10) of the first and second sections (16, 18) merge into one another, and wherein primary and secondary air in the primary and secondary air ducts (8, 10) are guided in countercurrent. Luftkonditioniervorrichtung after Claim 1 characterized by means for diverting a portion of the primary air from the primary air outlet (13) and supplying this branched primary air as secondary air into the secondary air inlet (14). Method for operating a Frischluftkonditioniervorrichtung after Claim 1 or 2 in summer operation with the method steps: - forming a thin liquid film of desiccant solution on the fabric and heat exchange surfaces (4) of the primary air ducts (8) in the second section (18); - forming a thin film of water on the heat exchange surfaces (4) of the secondary air ducts (10) in the first and second sections (16, 18); - Passing secondary air in the form of exhaust air from a room to be conditioned or in the form of an air stream, which is branched off from the primary air outlet in the secondary air ducts (10); and - directing the primary air in the form of fresh air from the environment through the primary air ducts (8) in countercurrent to the secondary air in the secondary air ducts (10), whereby the primary air in the second section (18) is dehumidified and pre-cooled and in the first section (16 ) is additionally cooled. Method for operating a Frischluftkonditioniervorrichtung after Claim 1 in winter operation with the method steps: - forming a thin liquid film of preheated desiccant solution on the fabric and heat exchange surfaces (4) of the primary air ducts (8) in the second section (18); - Forming a thin liquid film of preheated water on the fabric and heat exchange surfaces (4) of the first section (16) of the primary air ducts (8); and - passing the primary air in the form of cold outside air through the second section (18) in which the primary air is pre-wetted and preheated; and then passing the primary air through the first section (16) in which the already preheated and pre-moistened primary air from the second section (18) is further heated and further humidified. Luftkonditioniervorrichtung after Claim 1 or 2 characterized in that the mass and heat exchange reactor (2) comprises a third section (30) adjoining the second section (18) such that the third section (30) extends the primary air flow channels (10) such that the primary air inlet (12) opens into the third section (30) that the secondary air outlets (15) lead laterally out of the second section (18) such that the primary air ducts (8) in the third section (30) are each disposed between tertiary air ducts (32) are disposed between a tertiary air inlet (36) and a tertiary air outlet (38), and that the primary air channels (8) and the tertiary air channels (32) of the third section (30) are separated by vapor permeable heat transfer plates or membranes (34). Luftkonditioniervorrichtung after Claim 5 , characterized in that the tertiary air inlets (36) open laterally into the third section (30) and that the tertiary air outlets (38) lead laterally out of the third section (30). Method for operating an air conditioning device according to Claim 5 or 6 in the summer mode with the method steps: - forming a thin film of water on the heat exchange surfaces (4) of the secondary air channels (10) of the first and second sections (16, 18); - Carrying secondary air in the form of exhaust air from a room to be conditioned or in the form of an air flow branched from the primary air outlet in the secondary air passages (10) of the first and second sections (16, 18); Passing tertiary air in the form of exhaust air from a space to be conditioned in the tertiary air ducts (32) of the third section (30); Passing the primary air in the form of ambient fresh air through the primary air ducts (8) of the third section (30) in countercurrent to the tertiary air in the tertiary air ducts (32), thereby pre-dehumidifying and pre-cooling the primary air in the third section (30); Passing the primary air from the third section (30) into the primary air channels (8) of the second section (16), thereby pre-cooling the primary air in the second section (18); and - directing the primary air from the second section (16) into the primary air ducts (8) of the first section (16), thereby cooling the primary air to the desired temperature. Method for operating an air conditioning device according to Claim 5 or 6 in summer operation with the method steps: - forming a thin liquid film of desiccant solution on the fabric and heat exchange surfaces (4) of the primary air ducts (8) in the second section (18); - forming a thin film of water on the heat exchange surfaces (4) of the secondary air channels (10) of the first and second sections (16, 18); Passing secondary air in the form of exhaust air from a space to be conditioned or in the form of an air stream branched from the primary air outlet in the secondary air ducts (10) of the first and second sections (16, 18); Passing tertiary air in the form of exhaust air from a space to be conditioned in the tertiary air ducts (32) of the third section (30); Passing the primary air in the form of ambient fresh air through the primary air ducts (8) of the third section (30) in countercurrent to the tertiary air in the tertiary air ducts (32), thereby pre-dehumidifying and pre-cooling the primary air in the third section (30); Passing the primary air from the third section (30) into the primary air ducts (8) of the second section (18), thereby further dehumidifying and further cooling the primary air in the second section (18); and - directing the primary air from the second section (18) into the primary air ducts (8) of the first section (16), thereby cooling the primary air to the desired temperature. Method according to Claim 8 characterized in that forming a thin film of water on the cloth and heat exchange surfaces (4) of the primary air ducts (8) in the first section (16) whereby the primary air is humidified and additionally cooled. Method for operating a Frischluftkonditioniervorrichtung after Claim 5 or 6 in winter operation with the method steps: - forming a thin optionally preheated water film on the heat exchange surfaces (4) of the primary air ducts (8) of the first section (16); - Passing secondary air in the form of warm, possibly moist exhaust air from a room to be air conditioned in the secondary air ducts (10) of the first and second sections (16, 18); - Passing tertiary air in the form of warm, possibly moist exhaust air from a room to be air-conditioned in the Tertiärluftkanälen (32) of the third section (30); Passing the primary air in the form of cold fresh air from the environment through the primary air ducts (8) of the third section (30) in countercurrent to the tertiary air in the tertiary air ducts (32), thereby preheating and preheating the primary air in the third section (30) ; Passing the primary air from the third section (30) into the primary air ducts (8) of the second section (18), thereby further preheating the primary air in the second section (18); and - guiding the primary air from the second section (18) into the primary air ducts (8) of the first section (16), thereby humidifying and cooling the primary air. Method for operating a Frischluftkonditioniervorrichtung after Claim 10 in winter operation with the method steps: - passing secondary air in the form of exhaust air from a room to be conditioned in the secondary air ducts (10) of the first and second sections (16, 18); - forming a thin liquid film of highly dilute desiccant solution on the cloth and heat exchange surfaces (4) of the primary air channels (8) in the second section (30); - moistening and heating of the primary air guided in the primary air ducts (8) of the second section (18) from the primary air ducts (8) of the third section (30); and - forwarding the primary air from the primary air ducts (8) of the second section (18) into the primary air ducts (8) of the first section (16). Method according to Claim 11 characterized in that the secondary air flow from the secondary air outlet (15) of the second section (16) is connected to the tertiary air inlet (36) of the third section (30) such that the secondary air from the second section (18) passes through the third air as tertiary air Section (30) is guided. Device or method according to one of the preceding claims, characterized in that the desiccant solution is an aqueous solution of one or more metal salts and in particular an aqueous lithium chloride and / or potassium chloride solution. Device or method according to one of the preceding Claims 1 to 13 , characterized in that the desiccant solution is an aqueous solution of an alcoholic compound and in particular an aqueous glycol solution.

Images