HK40003907A - Air-conditioning via multi-phase plate heat exchanger - Google Patents

Description

The Commission

The use of air conditioning in the building is a major contributor to the global electricity supply and thus to the CO2 balance of the earth. Energy savings can be achieved by heat recovery, especially through heat exchangers. Heat is stored or transported not only in the heat capacity of the substances concerned but also in the enthalpy of the water vapor involved. Heat recovery can only be efficient if cooling and heating, condensation and evaporation take place simultaneously and in the same place.

State of the art

Air conditioning is preferably by electrically operated refrigeration in summer or by combustion of combustible substances in winter. To achieve a comfortable climate, water vapour must usually be removed from the air by condensation or added by evaporation. The energy expenditure required for this is in extreme cases many times that which would be required for mere cooling or heating the steam-free air over the same temperature range. The condensation water is discarded instead of being used for evaporative cooling.

The so-called regulated ventilation is intended to help save energy by using air/air heat exchangers. Although it is possible to bring the outside temperature almost to indoor temperature in winter, this heated fresh air is extremely dry and must be subsequently humidified with energy. In summer the problem is even worse: since the enthalpy difference between humid hot outdoor air and cool dry indoor air is much greater than the enthalpy difference between dry indoor air and the same air at outdoor temperature, such a heat exchange can always make only a very small contribution to reducing the required cooling power.

Therefore, patent A192/2015 describes an air/air heat exchanger where the condensate formed during cooling is fed from the fresh air into the exhaust air to evaporate into it, compensating the condensation heat released as evaporative heat.

However, it is not possible to cool the air below the temperature in the room to be air conditioned, which would be necessary to remove other heat inputs such as solar radiation or computer heat.

An additional problem is that constant humidification of heat exchanger surfaces can lead to the growth of bacteria or other microbes, which could then lead to constipation or even the transmission of disease.

A heat exchanger between intake and exhaust air as defined in claim 1 is known from DE 10 2010 011707 A1 where these two air streams are separated by a heat conducting wall with a hydrophilic surface on both sides, so that on one side hygroscopic liquid of warm moist air is absorbed by absorption of water vapour under heat release and that heat is evaporated through the separation wall on the other side in a colder air stream of water from a highly aqueous hygroscopic solution, heating the colder air and cooling the warmer air, while cooling the warmer air in the heat metamorphosis area by heating the area by heating the water-rich hygroscopic solution.

WO 2016/037232 A1 is an indirect evaporative cooler, where the evaporative cooler has a plate heat exchanger, where in a first flow path the air is passed through a dry area of the plate heat exchanger and at the end of the first flow path some of the air is passed through a second moist flow path in the opposite direction so that the evaporative cooling in the second flow path cools the air in the first flow path.

US 2005/0210907 A1 also has an indirect evaporative cooler, whereby the gas is partly directed into the second stream already in the first stream.

DE 20 33 206 A1 is a device for drying air in a multi-channel system, whereby the air is cooled and dried by evaporation in adjacent chambers.

WO 2004/085946 A1 is known to be a plate heat exchanger with a spray device for additional air cooling.

The task

In principle, a suitable heat exchanger should be able to achieve the full cooling capacity by evaporative cooling in summer, because the enthalpy difference between dry indoor air and steam saturated air at outside temperature must always be greater than the enthalpy difference between humid hot outdoor air and cool dry indoor air.

In many climatic situations, however, pure evaporative cooling is possible if only enough water is supplied to the heat exchanger on the exhaust side.

Conversely, for heating cold moist air in the cold season, it is possible to heat this air by hygroscopic drying.

The following are therefore the aims of the invention: Air conditioning of rooms by evaporative cooling or heating by hygroscopic air drying for different climatic conditions of the outdoor environmentHeat exchanger hygiene conditionsControl of humidity in the rooms to be air conditioned by hygroscopic solution or water evaporationRegeneration of the hygroscopic solution after absorption of this water, possibly resulting in crystallization processes which must not interfere with the whole process, by the same apparatus

Resolution of tasks and sub-tasks and expected results

The task of providing room air conditioning by pure evaporative cooling or heating by hygroscopic air drying is accomplished according to the invention by a novel multiphase plate heat exchanger and a method for operating such a heat exchanger as described in claim 1 and claim 5 respectively.

A multiphase plate heat exchanger is a plate heat exchanger for two gaseous media of different temperature and vapour content, moving in the opposite or parallel current of each controllable blowing, whereby the active heat transfer surface between the affected media on one or both surfaces is moistened by one or two different slow-flowing fluids, which are in direct interaction with the respective media, so that evaporation or condensation and the resulting changes in concentration in the fluids may also result in crystallisation or solution of crystals, whereby these fluids flow from the outside to their specific positions between the heat pump platforms, and are subjected to the same curvature and the same effects of gravity, heat transfer and fluid deposition, and not more frequently than in the plate films, due to the presence of gravity and gravity.

In order to operate such a multiphase heat exchanger successfully, the additional task of introducing the fluids in question into the columns of the heat exchanger by drip, but the amount of fluid to be introduced per column should not vary greatly, is given. the supply of liquid from a storage tank to the input positions between the heat exchanger plates is made so that the supply line to the pump is connected to a bundle of capillary tubes or hoses which terminate at the appropriate destinations in the heat exchanger.The supply of liquid from a storage tank to the input positions between the heat exchanger plates is made so that the supply line to the pump leads to a common connection channel between the heat exchanger platesThe connection channel is formed by congruent corresponding air gaps through these plates, with each plate droplet into which the liquid is introduced being tested for the effect of the liquid flowing through the gaps. It is recommended to maintain a low pressure pressure pressure droplet on the plate before the flow of the liquid is started, in order to prevent the flow of the liquid from the bottom of the plate.

Experiments have shown that although the capillary fluid supply is much more complex and expensive than the alternative of a common connection channel across all plates, the uniform distribution of fluid across all plates is much more accurate, which significantly improves the efficiency of the system.

Experiments have also shown that the exact dosage of the liquids to be supplied by capillaries or nozzles alone is very imprecise, because the smallest impurities can change the flow resistance and therefore the flow rate at the same pump strength.

Once the specified fluids have been introduced into the surface of the plates in the correct quantity, the next task is to wet these plates evenly.

This is achieved by the fact that the surfaces of the active heat transfer surfaces favour the uniform distribution of the liquid film or the local retention of crystals or their transport by grooves, fine porous surface, abrasion, scratches and/or fibre coating, as well as coatings by hydrophilic materials or by a combination of several such measures.

To solve the problem of regulating the humidity in the rooms to be air conditioned by means of a hygroscopic solution or evaporating water, on the one hand, an isoenthalpic transition is possible and, on the other hand, additional heating or cooling may be necessary. An isoenthalpic transition can be achieved in the multiphase heat exchanger of the invention by introducing the same air flow into the primary and secondary sides of the said heat exchanger so that both these streams flow parallel and in the same direction, using the same fluid to moisten the heat exchanger surfaces in both streams. This is water, so an isoenthalpic transition of the air flow is achieved while simultaneously heating the water. In the first case, this is achieved by maintaining a hygroscopic fluid in the second solution.

If, on the other hand, the air stream is cooled by a hygroscopic solution during dehumidification, additional cooling of the heat exchanger by another medium may be useful, and the multiphase heat exchanger of the invention may be used, the air to be dehumidified being introduced in the opposite stream on the primary side together with a hygroscopic solution moistening the heat exchanger surface and the medium to be cooled, which may flow in direct or in opposite current as required and which may be gaseous or liquid, on the secondary side.

The reverse case, that of a stream of air becoming hotter when it is moistened, is for example the case of the task of regenerating the hygroscopic solution after it has absorbed water.

Both tasks can be accomplished simultaneously if the multiphase plate heat exchanger described in this annex has the media or fluid streams or individual sections of the heat exchanger itself in direct contact with separate heating media or an electric heater conducting heat to heat or cool these areas.

The installation of an external heating system and its space requirements underline the importance of the above-mentioned task of finding the most compact possible design for the whole apparatus, which is achieved by combining a multiphase heat exchanger with two or more plate heat exchangers for heating or cooling purposes, the combination being a single plate package, each of which forms congruent areas on the plates of the package.

The task of ensuring hygienic conditions in the heat exchanger and the task of limiting humidity in the rooms to be air conditioned by means of a hygroscopic solution is jointly solved in such a way that the liquids used to moisten the active surfaces in the multiphase plate heat exchanger may contain water or other solvents, hygroscopic salts, refrigerants, disinfectants or net agents. The above-mentioned coating of the heat transfer surfaces with Ti02 nano crystals has an additional positive effect in this context. The known photocatalytic properties of TiO2 ensure that when illuminating the thermal surface surfaces, organic materials or microbes which would normally be exposed to light at the surface are dissolved by chemical substances and for this purpose a transparent or plastic layer must be made of the material or methane, the transparent or plastic layer must be removed from the surface of the heating surface.

In summary, the task of air conditioning rooms by pure evaporative cooling and limiting the humidity in the air-conditioned rooms by a hygroscopic solution is solved in such a way that in a multiphase plate heat exchanger the primary medium is the hot and humid outdoor air of a living room and the secondary medium is the consumed but relatively dry and cool air of the living room flowing in the opposite direction to the primary medium and that the inner surfaces of the plate spaces for the primary medium are treated with a hygroscopic solution, with this liquid and the air flowing in the opposite direction while the inner surfaces of the plate air are heated for the secondary medium, which is maintained by water evaporation. However, if the temperature of the room is as low as possible, the temperature can be achieved by means of a significantly lower temperature, which is closely related to the temperature of the room, the temperature of the air heater can be maintained.

The task of heating a room by hygroscopic air drying is solved in such a way that in a multiphase plate heat exchanger the primary medium is the cold outside air of an inhabited room and the secondary medium is the used but relatively humid and warm air of the inhabited room, which flows in the opposite direction to the primary medium, and that in this case the inner surfaces of the plate slits are used for the secondary medium with hygroscopic solution, whereby this liquid and air flow in the opposite direction instead of the normal one, while the inner surfaces of the plate slits for the primary medium are used for the pressure relief of water, which can flow in any direction. This ensures that a fresh air is supplied with a suitable room temperature but at a much lower temperature than the active water supply.

The secondary condition of the task of air conditioning rooms by evaporative cooling, or heating by hygroscopic air drying, was to solve this task for different climatic conditions of the external environment. This is achieved by combining several of the above multiphase exchangers into a system. For example, for cooling in a room with dry air, it may be useful to first humidify the exhaust air in a multiphase exchanger for isoenthalpic evaporation before performing the previously described cooling process.

Conversely, in a humid tropical climate, it is advantageous to pre-dry the fresh air in a multiphase heat exchanger for isenthalpy drying before entering the cooling process described above.

The ability to heat or cool a room without visible energy is by no means a perpetual motion machine. A hygroscopic saline solution is a highly efficient energy carrier. For example, a concentrated LiCl solution can absorb 10 to 15 times its own volume of water from humid air. The resulting condensation heat that can be released from a liter of concentrated LiCl solution is therefore about as large as the amount of heat generated by burning a liter of heating oil.

The task of regenerating the hygroscopic solution by a similar apparatus after this solution has absorbed water and thereby become diluted and ineffective is solved by a multiphase plate heat exchanger where the primary medium is hot and humid outdoor air and where the inner surfaces of the plate slits for the primary medium are moistened with a preheated, diluted and slightly hygroscopic solution in the flow opposite to the primary medium and where the secondary medium which flows into the primary medium in the current is the same air which has been additionally heated and almost evaporated after the primary passage through the heat exchanger, thus condensing the inner surfaces of the plate for the secondary medium and cooling the secondary medium by the heat of its discharge, which forms on the same air, which is cooled by the heat flow in the same medium.

Since the desiccation process described for the regeneration of the hygroscopic solution cannot be excluded, salt crystals may be formed which, if carried away from the heat exchanger by the flow, could possibly lead to blockages of the system, it is desirable as an additional task that such crystals remain at the place of their formation, where they are then dissolved by condensation water again in the next cooling phase, provided that this takes place in the same apparatus.

Listing of the figures and the meaning of the numbers

Figures 1a to 1d show four different ways of using a multiphase plate heat exchanger, namely: 1a shows a schematic representation of a single-stage refrigerator with multiphase plate heat exchanger and hygroscopic air dryingFig.1b shows the solution regeneration using the same apparatusFig. 1c shows the isoenthalpic air humidification and cooling by means of a multiphase plate heat exchangerFig. 1d shows the isoenthalpic air drying and heating by means of a multiphase plate heat exchangerFig. 2a and 2b show projections across the plates with the conduction of primary and secondary media and the liquid methacrylate layers adjoining the air heat exchangerFig. 2a shows a vertical plate wicking and liquid methacrylate methacrylate methacrylate conduction by means of a multiphase plate heat exchangerFig. 2d shows a horizontal conduction of a multiphase plate heat exchanger. Fig. 4a shows a multiphase plate with a multiphase heat exchanger and a multiphase plate with a multiphase heat exchanger.

The numbers in the figures mean:

A...environmentB...air conditioned room1...gas primary medium1a...plate cavities for primary medium2...gas secondary medium2a...plate cavities for secondary medium3...liquid for wetting the inner walls of primary medium metamaterial cavities4...liquid for wetting the inner walls of secondary medium metamaterial cavities5...capillaries for feeding primary medium liquid6...pipe for removing primary medium liquid7...capillaries for feeding secondary medium metamaterial cavities8...multi-plate cavity for removing secondary medium metamaterial cavities9...flat-air cavity10...capacitor for heating liquid and water cavities10...capacitor for heating liquid and water cavities10...capacitor for heating liquid and water cavities10...capacitor for heating liquid and water cavities10...capacitor for heating liquid and water...capacitor for heating liquid and water...capacitor for heating liquid and water...capacitor for heating liquid and water...capacitor for heating liquid and water...capacitor for heating liquid and water...capacitor for heating liquid...capacitor for heating...capacitor for heating...capacitor for heating...capacitor for heating...capacitor for heating...capacitor for heating...capacitor for heating...capacitor for heating...capacitor for heating...capacitor for heating...capacitor for heating...capacitor for heating...capacitor...capacitor...capacitor...capacitor...capacitor...capacitor...capacitor...capacitor...capacitor...capacitor...capacity...capacitor...capacity...capacity...capacity...capacity...capacity...capacity...capacity...capacity...capacity...capacity...capacity...capacity...capacity...capacity...capacity...c

Description of the drawings

Fig.1a shows how the multiphase plate heat exchanger of the invention is used for a ventilation system with cooling function in a warm humid climate. The multiphase plate heat exchanger -14-, which in reality usually consists of many chambers formed by plates, is conceptually represented by two adjacent chambers -14a, 14b- separated by an active surface -13a- with the upper two chambers -14a- representing the primary columns of the heat exchanger and the lower -14b- the secondary columns of the heat exchanger.17b- in contact. Water vapour condenses in the solution -17a- and the resulting heat is discharged through the active surface -13a- to the secondary side -14b- of the heat exchanger. Fresh air -15- cooled to room temperature and dehumidified is directed to the room to be cooled. The hygroscopic solution -17b- diluted by water condensation leaves the heat exchanger -14- and is then fed into the regeneration described in Fig. 1b. On the secondary side -14b- dry air -16-18- is brought into contact with water -18- from the room to be cooled, while the primary condition -14a- is used to cool the heat from the water -15 - and the heat from the exhaust -15 - is available from the primary condition -14a- of the heat exchanger.This heat is then removed from the primary side -14a-, which results in a cooling effect on the fresh air, while the remaining water -18- is only slightly heated and flows back into a storage tank.

Figure 1b shows as another example of the use of the multiphase plate heat exchanger -14- the regeneration of the hygroscopic solution -17b, which is diluted by the cooling process in Figure 1a and thus unusable. This corresponds to an energy-efficient form of desalination of water for which there are also a large number of applications. On the primary side -14a- fresh air -15- is brought into contact with heated diluted hygroscopic solution -17c- - the heating is not shown - whose temperature must be so high that its vapour pressure is higher than the vapour pressure of the fresh air -15-.The secondary side -14b- is used to recover the condensation heat energy which is generated by the hot, steam-saturated air -15c- being directed to the secondary side of the heat exchanger -14b- where it is removed from the primary side -14a- by heat, thus cooling it and the resulting excess heat from the active F-1913a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-a-However, as a rule, the vapour content of the moistened fresh air -15- after leaving the primary side -14a- will not be sufficient to maintain the energy recovery process described permanently.

Figure 1c shows the isoenthalpic humidification and cooling of fresh air -15 by means of a humidifier-14c, in the form of a multiphase plate heat exchanger-14. The incoming fresh air -15- is first divided into 2 streams, which are directed parallel to each other to the primary side -14a and secondary side -14b - of a humidifier-14c, in the form of a multiphase plate heat exchanger-14, where it is brought into contact with water -18-, which humidifies the active surfaces -13a and may move in any direction.

Fig. 1d shows the isoenthalpic drying and heating of fresh air -15 by means of an air dryer -14d, in the form of a multiphase plate heat exchanger -14. The incoming fresh air -15- is first divided into 2 streams, which are directed parallel to each other to the primary side -14a and secondary side -14b- of an air dryer -14d, in the form of a multiphase plate exchanger -14 where they are heated with hygroscopic solution -17a, 17b- which moistens the active surfaces -13a- and is intended to move preferably in the opposite direction to the fresh air -15- in contact with it.

Fig. 2a shows a schematic cross-section of the plates of a multiphase plate heat exchanger with liquid conduction through the pumps -11, 12 and the capillaries -5,7 acting as throttles in a case where the fluid path is mainly determined by gravity, i.e. a situation where vertically placed plates are recommended, since in each heat exchanger plate gap - 1a,1b- furthermore both adjacent surfaces can be easily wrapped with liquids -3,4 , whereby the conduction of primary -1, and secondary medium -2, as well as the fluid conduction layers -3,13 - which are used as throttles, are marked e4. This is a situation where the fluid conduction is largely controlled by gravity, i.e. a similar fluid conduction system -5,6,18 - is always guaranteed to be efficient for the discharge of liquid, especially if the plate is not floating or if it is only moving with a fluid or liquid, or if the liquid is being discharged from a liquid or liquid, or its residual material, or if it is not being discharged by a liquid or liquid, or a liquid, or a liquid, or a liquid, or a liquid, or a liquid, or a liquid, or a liquid, or a liquid, or a liquid, or a liquid, or a liquid, or a liquid, or a liquid, or a liquid, or a liquid, or a liquid, or a liquid, a liquid, or a liquid, or a liquid, a liquid, or a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a liquid, a, a liquid, a, a, a, a, a, a, a, a, a, a, a, a, a, a, a, a, a,

Fig. 2b shows a schematic cross-section of the plates of a horizontal multiphase plate heat exchanger with liquid conduction through the pumps - 11, 12 and connection channels -9, 10 - through the heat exchanger plates -13 - whereby at the breaches through the gaps of the corresponding medium -1, 2 -1, 2 -1, 2 -1, 2 -1, 3 -1, 3 -2, 3 -4, -4, -5, -5, -5, -5, -6, -6, -6, -6, -7, -8, -8, -8, -8, -8, -8, -8, -8, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -9, -

Figure 3 shows the diagram of a three-stage cooling system between the hot ambient air -A- and the air in the room -B- to be cooled, consisting of a multiphase plate heat exchanger -14 and two isoenthalpic humidifiers -14c and -14c' which have a design similar to those shown in Figure 1. The fresh air -A-15- coming from the environment is directed on the primary side -14a- of the multiphase plate heat exchanger -14-che through the surface -13a-based hygroscopic solution -17a, 17b- which moves in the direction of the -15-metha-cooling air. The heat flowing through the surface -13c is diverted to the outer air flow -1416 - where the surface -13A-heat is discharged to the outer air flow -14-seconds, where the surface -13-metha-cooling air moves in the direction of the -15-metha-cooling air.Since the active surface -13a- is moistened on the secondary side -14b- with water -18 which is offered in excess, exactly as much water -18- is evaporated into the exhaust air -16- on the secondary side -14b- as the heat supply from the primary side -14a- is. This exhaust air -14- flowing into the multiphase plate heat exchanger -14- is already colder and wetter than the air in the air conditioned room -B- since it has already passed the isolated humid air -14c- where it has been cooled and moisturized by absorbing water -18- to the tapered surface of the air conditioned room -B-16.On the other hand, the fact that exhaust air -16- enters the multiphase plate heat exchanger -14- at the temperature of the dew point of the air-conditioned room -B- allows the now dried fresh air -15- to have a temperature close to this dew point when it leaves the multiphase plate heat exchanger -14- This cold dry fresh air -15- is now directed to the isoenthalpic humidifier -14c', where it is brought by re-humidification with water -18- to a temperature significantly below that of the air-conditioned room -B-.

Fig. 4 shows the diagram of a three-stage heating system between the cold ambient air -A- and the air in the room -B- to be heated, consisting of a multiphase plate heat exchanger -14- an isothermal air humidifier -14c- and an isothermal air dryer -14d- which have been shown in the same way as in Fig. 1c and Fig. 1d. The fresh air -15- from -A is heated on the primary side -14a- in the multiphase plate heat exchanger -14- by the active surface -13a-wetting water -18-, which is heated in the overhead section. The heated surface is heated by the active surface -13a-wetting air -14- from the outer surface -14-A -14- where the heat is directed outwards towards the outer surface -14-B.Since the active surface -13a- on the secondary side -14b- is moistened with hygroscopic solution -17a, 17b- moving in the direction of the exhaust -16- on the primary side -14a- exactly as much water -18- evaporates into the fresh air -15 as the heat supply from the secondary side -14b- This is already slightly colder and wetter than the air in the air conditioned room -14b- as it has already passed the iso-enthalpy humidifier -14c, where it has been moistened by absorbing water -18- to the optimum, which can be calculated from one half of the humidity level of each air.In practice, automatic control by a programmable chip in combination with appropriate temperature and humidity sensors and flow meters is recommended. The control in this case works by the amount of water -18-in relation to the airflow -16 - injected. The advantage of this humidification in the isoenthalpic humidifier -14c- is that there is then enough water vapour available to allow complete humidification of the fresh air -15 - by its subsequent condensation in hygroscopic solution -17a,17b- in the multiphase plate vaporizer -14- so that the fresh -15 - leaves the multiphase plate vaporizer -14 - with a vapor that is far below the temperature of the air -14 - and is directed to the room -14 - which is not isolated and is not maintained -14 - and the air -15 - is directed to the room -14 - which is not isolated -14 - and is not maintained -15 - in the room -14 - which is not maintained -15 - and the air -15 - is directed to the room -14 - which is not.where it is dried by hygroscopic heating with solution -17a, 17b- and can then be used to heat the air-conditioned room -B-.

Fig. 5 shows a scheme in which the steam supply for the solution regeneration of Fig. 1b is achieved by an air humidifier -14c- constructed in the same way as Fig. 1c, but without the use of isothermal energy because hot water is supplied.

However, a humidifier -14c- of the type of the multiphase plate heat exchanger -14- described here proves particularly effective for the task of regenerating hygroscopic solution, since it consumes only exactly the amount of steam needed for the process minus the recoverable condensation heat. The drying of the hygroscopic solution -17c,17a- which moistens the active surface -13a- is made possible on the primary side -14a- of the multiphase plate heat exchanger -14- by the fact that on its secondary side -14b- condensing water vapour -19- provides the necessary process heat.The hot and very humid air -15- from the primary side -14a of the multiphase plate heat exchanger -14- is therefore directed to a humidifier -14c- where it is brought into contact with hot water -18a- in the opposite direction. The fresh air -15- is further heated and saturated with steam. Once it is then directed back into the multiphase plate heat exchanger -14- on its secondary side -14b, just as much water vapor condenses as is necessary to maintain the dry pressure on the primary side -14a of the multiphase plate heat exchanger -14c.The temperature of the fresh air leaving the multiphase plate heat exchanger -14- -15- is as close as possible to the temperature it had before the whole process.

Claims (13)

1. Multiphase plate heat exchanger (14) for two or more gaseous media (1,2), wherein the multiphase plate heat exchanger (14) comprises a plurality of chambers (14a, 14b) formed by heat exchanger plates (13) separated from each other by active surfaces (13a), wherein the active surfaces (13a) are adapted for heat transfer between the affected media (1, 2) on one or both surfaces of one or two different slow-flowing liquids (3, 4), so that they interact directly with the respective media (1, 2), so that evaporation or condensation and also crystallization or solution of crystals can take place due to the concentration changes in the liquids occurring thereby, wherein pumps (11, 12) are provided in order to transfer these liquids (3, 4) from the outside to their specific input positions (9a, 10a) between the heat exchanger plates (13) so that they can move from there as a wetting liquid film along the active surfaces (13a) through the plate heat exchanger (14), wherein associated media (1, 2) and liquids (3, 4) can flow in parallel or countercurrent to each other, characterized in that the liquid supply from a storage tank to the small openings (9a, 10a), which serve as input positions between the heat exchanger plates (13), is effected in such a way that the supply line after the pump (11, 12) fans out into a bundle of capillaries (5, 7) in tubular or hose form which open out at the corresponding small openings (9a, 10a) in the heat exchanger, and in that in each heat exchanger plate gap (1a, 1b) both adjacent surfaces can be wetted with the liquids (3, 4).
2. Multiphase plate heat exchanger (14) according to claim 1, characterized in that the inflows for media (1, 2) or liquids (3, 4) or individual sections of the heat exchanger (14) itself are in heat-conducting contact with separate tempering media or an electric heater which can heat or cool these regions.
3. Multiphase plate heat exchanger (14) according to one of the preceding claims, characterized in that the surfaces (3, 4) of the active surfaces (13a) for heat transfer permit the uniform distribution of the liquid film (3, 4) or the local retention of crystals or their further transport mechanically by grooves, finely porous surfaces, grinding marks, scratches and/or fiber coating, as well as by hydrophilic materials and coatings or also by a combination of several such measures.
4. Combination of several of the multiphase plate heat exchangers according to one of the preceding claims, characterized in that said combination consists of a single plate pack and the individual partial heat exchangers each form congruent regions on the plates of said pack.
5. Method for operating a multiphase plate heat exchanger (14) according to claim 1, comprising two or more gaseous media (1,2) moved in countercurrent or parallel flow by one or more controllable blowers, at different temperatures and with different vapor content, wherein the active surfaces (13a) for heat transfer between the media concerned (1, 2) are wetted on one or on both surfaces by one or two different slow-flowing liquids (3, 4) which are in direct interaction with the respective media (1, 2), so that evaporation or condensation and, due to the concentration changes in the liquids occurring thereby, crystallization or solution of crystals can also take place, wherein these liquids (3, 4) are pumped from the outside to their specific input positions (9a, 10a) between the heat exchanger plates (13) and from there move as a wetting liquid film along the active surfaces (13a) through the plate heat exchanger (14), wherein associated media (1, 2) and liquids (3, 4) can flow in parallel or countercurrent to each other, characterized in that the liquid supply from a storage tank to the small openings (9a, 10a), which serve as input positions between the heat exchanger plates (13), is effected in such a way that the supply line after the pump (11, 12) fans out into a bundle of capillaries (5, 7) in tubular or hose form which open out at the corresponding small openings (9a, 10a) in the heat exchanger, and in that in each heat exchanger plate gap (1a, 1b) both adjacent surfaces are wetted with the liquids (3, 4).
6. Method according to claim 5, characterized in that the said liquids (3, 4) may contain water or other solvents as well as hygroscopic salts, refrigerants, disinfectants or wetting agents.
7. Method according to claim 5 or 6, characterized in that the primary medium (1) is the hot and humid fresh air (15) of the ambient environment of a room to be cooled and the secondary medium (2) is the used dry and cool exhaust air (16) of this cooled room, which flows in countercurrent to the primary medium (1), and in that the inner surfaces of the plate gaps (1a) for the primary medium are wetted with hygroscopic solution (17a), wherein the liquid (3) and primary medium (1) flow in opposite directions, while the inner surfaces of the plate gaps (2a) for the secondary medium (2) are wetted with water (18) which can flow in any direction.
8. Method according to one of claims 5 to 7, which serves to regenerate diluted hygroscopic solution, characterized in that the primary medium (1) is the hot and moist fresh air (15) of the ambient environment of a room to be cooled and in that the inner surfaces of the plate gaps (1a) for the primary medium (1) are wetted with additionally preheated diluted hygroscopic solution (17c) according to claim 2 in countercurrent to the primary medium (1), and in that the secondary medium (2) which flows in countercurrent to the primary medium (1) is the same but heated fresh air (15c) which is heated after the primary passage through the multiphase heat exchanger (14) and is virtually saturated with additional steam (20), and in that condensation forms on the inner surfaces of the plate gaps (2a) for the secondary medium (2) during the cooling thereof, which condensation leaves the multiphase heat exchanger (14) cooled in direct flow with the secondary medium (2).
9. Method according to one of claims 5 to 8, comprising a combination of two multiphase plate heat exchangers, characterized in that exhaust air (16) from a room (B) to be cooled is isoenthalpically humidified and cooled to its dew point in a first multiphase plate heat exchanger (14) serving as an air humidifier (14c), and is then humidified and heated on the one hand by water (18) in a second multiphase plate heat exchanger (14), and on the other hand is conducted in countercurrent to hot moist fresh air (15) coming from the ambient environment (A), which is simultaneously dried by a hygroscopic solution (17a, 17b) and cooled to close to the dew point of the room (B) to be cooled.
10. Method according to claim 9, comprising a third multiphase plate heat exchanger according to one of the claims from 1 to 4, characterized in that the dried fresh air (15) coming from the second multiphase plate heat exchanger (14) and cooled to close to the dew point of the room (B) to be cooled is further isoenthalpically cooled in the third multiphase plate heat exchanger (14) serving as air humidifier (14c).
11. Method according to one of claims 9 or 10, comprising a multiphase plate heat exchanger (14) serving as an air dryer (14d) according to one of claims 1 to 4, characterized in that the warm moist fresh air (15) from the ambient environment (A) is first pre-dried in a multiphase plate heat exchanger (14) serving as an air dryer (14d) under isoenthalpic heating by means of hygroscopic solution (17a, 17b) before it is cooled in the actual multiphase plate heat exchanger (14) in countercurrent to the exhaust air (16) and further dried with hygroscopic solution (17a, 17b).
12. Method according to one of claims 5 to 8, comprising a combination of three multiphase plate heat exchangers according to one of claims 1 to 4, characterized in that exhaust air (16) of a room (B) to be heated is isoenthalpically humidified in a first multiphase plate heat exchanger (14) serving as an air humidifier (14c) and then dried in a second multiphase plate heat exchanger (14) on the one hand with hygroscopic solution (17a, 17b) and is conducted on the other hand in countercurrent to cold fresh air (15) coming from the ambient environment (A), which fresh air is simultaneously humidified by water (18) and heated by drying the exhaust air (16) and where said humidified and slightly heated fresh air is isoenthalpically dried and heated in a third multiphase plate heat exchanger (14) serving as an air dryer (14d) and from there is supplied to the heating of the room -B-.
13. Method according to one of claims 5 to 8, comprising a combination of two multiphase plate heat exchangers according to one of claims 1 to 4, which serves to regenerate diluted hygroscopic solution (17b) to convert it back into concentrated hygroscopic solution (17a) by dehydration, characterized in that fresh air (15) is fed into the primary side (14a) of a first multiphase plate heat exchanger (14), where it flows in countercurrent to heated diluted hygroscopic solution (17c) wetting the active surface (13a) of said multiphase plate heat exchanger (14), and after it is heated thereby and almost saturated with moisture it reaches a second multiphase plate heat exchanger (14) serving as an air humidifier (14c), where the active surface (13a) is wetted with hot water so that the fresh air (15) is further heated and humidified, and where said fresh air (15) is thereafter passed again to the first multiphase plate heat exchanger (14), but to its secondary side (14b), where it cools again and condenses the excess steam on the active surface (13a) of said first multiphase plate heat exchanger (14), thereby providing the heat required for dehydration from the diluted hygroscopic solution (17b).