EP2605691B1 - Method and device for drying humid air - Google Patents

Description

Background of the invention

The invention relates to a method for drying moist air from a working space of a water-conveying machine, in particular a dishwasher, as well as a device for drying moist air from a working space of a water-bearing machine.

Dishwashing machines and tumble dryers for domestic or commercial use belong to the field of water-conducting machines or appliances. These machines are often designed for installation in a row of kitchen cabinets and have a device door on their front. There is a skirting board under the appliance door.

Both dishwashers and dryers usually use rinsing or drying programs, which are specified by a controller of the device and then processed by the components installed in the device. As components of the devices are in particular pumps, blowers, valves or about to call a heater.

In dishwashers, these programs to be processed include, in particular, program steps in which a rinsing liquid, for example water mixed with rinsing agent, is distributed by a circulating pump via dishes in the working space of the appliance and subsequently conveyed out of the working space into a lye outlet. The completion of a rinse is a program section drying, in which the drying of the dishes, the moisture must be brought out of the work space as much as possible.

The same task of drying material that is in the workspace arises with a tumble dryer.

For drying systems are known, which operate on the recirculation or exhaust air principle or combined with both principles.

In the extract air drying system, workspace ventilation supports the drying process by removing moist air from the work area to the environment of the unit. At the same time, the process air in the working area is admixed with cold ambient air. It requires an opening on the device, especially in its door or baseboard.

The known circulating air drying systems use condensing surfaces in a circulating air circulation system for the drying process. As condensation surfaces, the comparatively cool outer surfaces of the device are used or the inner surfaces of the working space itself. Furthermore, it is known to cool these condensation surfaces with fresh water. The humid air itself is heated up as much as possible in the working area so that it can absorb a high level of water vapor. In order to achieve good and especially excellent drying results, it is necessary in known devices that they work with a temperature of humid air in the working space of about 65 degrees Celsius (° C).

Out DE 103 34 792 A1 is a dishwasher with a washing known. For drying the items to be washed, the washing container is connected in an air-conducting manner to a line system in which a Peltier element is arranged. The Peltier element is used for cooling and thereby drying and heating air conducted through from the washing. Downstream of the Peltier element, a capacitor and subsequently a heater are arranged. In the sub-program step rinsing, the material to be treated is warmed to about 50 ° C or even lower.

Out WO 01 85003 A2 a drying device for drying dishes in a dishwasher is known. For this purpose, hot, moist Spülraumluft arising in the wash compartment is dehumidified by condensation outside the wash compartment in a heat exchanger. The heat exchanger comprises a water guiding space and adjacent thereto an air duct for Spülraumluft. For drying, cold water is introduced into the water supply room and hot, humidified Spülraumluft passed through the air duct. In the process, condensate from the humidified purge room air in the air guide chamber is deposited on a heat exchanger surface. In order to maintain this condensation effect, heated water is repeatedly discharged from the water-guiding space and fed into it with fresh cold water.

Underlying task

The invention has for its object to provide a method and apparatus for drying humid air, which allow compared with known devices as possible better drying results at the same time lower operating costs.

Inventive solution

This object is achieved with a method for drying moist air from a working space of a water-bearing machine with the features of claim 1, in particular a dishwasher, with the steps: providing the moist air in the working space with a temperature between 40 ° C and 50 ° C, providing a cooling medium in a heat exchanger with a temperature of less than 20 ° C and passing the thus tempered, humid air from the working space through the heat exchanger.

According to the invention, the air in the working space for drying is tempered only comparatively low. This is in contrast to conventional methods where initial drying temperatures of typically between 65 ° C and 70 ° C is worked. As a result, a large amount of heating energy is saved according to the invention, because in the mentioned devices each degree of heating requires on average a heating power of several watts. At the same time, a heat exchanger is used in the invention, which is arranged separately from the working space and in which a particularly efficient dissipation of heat from the moist air takes place. As a result, a particularly high proportion of water vapor from the moist air condenses and excellent drying results are achieved without high energy consumption. For this purpose, the heat exchanger water at a temperature of below 20 ° C is supplied.

As a cooling medium in the heat exchanger according to appropriate tempered fresh water is provided. Alternatively, it is also advantageous to store stored residual water at temperatures which may initially also be above 20 ° C. from a previous rinse cycle.

The cooling medium is cooled according to the invention before it is provided in the heat exchanger. To cool the cold of a cold and heat generating device is advantageously used, the heat is also used for heating.

Furthermore, the cooling medium is advantageously cooled by means of a circuit on an ice storage. The ice storage tank serves as a cold storage, which can be supplied with energy in due time, depending on the desired program progression.

In the heat exchanger, a heating medium is preferably provided, wherein the moist air from the working space in the heat exchanger, in particular initially past the cooling medium and subsequently past the heating medium. The air is thus advantageously dehumidified by cooling and subsequently preheated again for receiving water vapor in the working space again.

The object is further achieved with a device for drying moist air from a working space of a water-bearing machine with the features of claim 5, in particular a dishwasher, which is adapted to the humid air in the working space provide a temperature between 40 ° C and 50 ° C to provide a cooling medium in a heat exchanger with a temperature of less than 20 ° C and to direct the so tempered, moist air from the working space through the heat exchanger.

As the cooling medium in the heat exchanger according to tempered fresh water is preferably provided.

The cooling medium is cooled according to the invention before it can be provided in the heat exchanger.

In this case, the cooling medium is particularly preferably cooled by means of a cycle on an ice storage.

In the heat exchanger, a heating medium is further preferably provided, wherein the moist air in the heat exchanger, in particular initially can be passed past the cooling medium and subsequently to the heating medium.

Brief description of the drawings

Fig. 1

eine perspektivische Ansicht einer Geschirrspülmaschine mit einem ersten Ausführungsbeispiel einer erfindungsgemäßen Vorrichtung zum Trocknen von feuchter Luft,

Fig. 2

eine Ansicht gemäß Fig. 1 eines zweiten Ausführungsbeispiels einer erfindungsgemäßen Vorrichtung zum Trocknen von feuchter Luft,

Fig. 3

eine Seitenansicht des Innen- und des Außenteils eines ersten Ausführungsbeispiels eines Wärmetauschers einer Vorrichtung gemäß den Fig. 1 oder 2,

Fig. 4

eine Ansicht gemäß Fig. 3 eines zweiten Ausführungsbeispiels eines Wärmetauschers einer Vorrichtung gemäß den Fig. 1 oder 2,

Fig. 5

ein Schema einer ersten Ausführungsvariante einer Vorrichtung gemäß den Fig. 1 oder 2,

Fig. 6

ein Schema gemäß Fig. 5 einer zweiten Ausführungsvariante einer Vorrichtung gemäß den Fig. 1 oder 2,

Fig. 7

ein Schema gemäß Fig. 5 einer zweiten Ausführungsvariante einer Vorrichtung gemäß den Fig. 1 oder 2,

Fig. 8

ein Schema gemäß Fig. 5 einer dritten Ausführungsvariante einer Vorrichtung gemäß den Fig. 1 oder 2,

Fig. 9

ein Diagramm des zeitlichen Verlaufs der Temperatur der feuchten Luft in einem Arbeitsraum einer Geschirrspülmaschine gemäß den Fig. 1 oder 2,

Fig. 10

eine perspektivische Ansicht einer Einrichtung zum Erzeugen von Kälte und Wärme einer Vorrichtung gemäß den Fig. 1 bis 9,

Fig. 11

eine perspektivische Seitenansicht einer Geschirrspülmaschine mit einer Einrichtung gemäß Fig. 10,

Fig. 12

die Ansicht XII in Fig. 11,

Fig. 13

ein Diagramm des zeitlichen Verlaufs der Temperaturen an einem Phasenwechselmaterial einer Einrichtung gemäß den Fig. 10 bis 12,

Fig. 14

eine prinzipielle Rückansicht eines weiteren Ausführungsbeispiels einer Geschirrspülmaschine mit einer erfindungsgemäßen Vorrichtung und

Fig. 15

teilweise die Ansicht XV in Fig. 14.

Exemplary embodiments of the solution according to the invention will be explained in more detail below with reference to the attached schematic drawings. It shows:

Fig. 1

a perspective view of a dishwasher with a first embodiment of an inventive device for drying humid air,

Fig. 2

a view according to Fig. 1 a second embodiment of a device according to the invention for drying moist air,

Fig. 3

a side view of the inner and the outer part of a first embodiment of a heat exchanger of a device according to the Fig. 1 or 2 .

Fig. 4

a view according to Fig. 3 a second embodiment of a heat exchanger of a device according to the Fig. 1 or 2 .

Fig. 5

a schematic of a first embodiment of a device according to the Fig. 1 or 2 .

Fig. 6

a scheme according to Fig. 5 a second embodiment of a device according to the Fig. 1 or 2 .

Fig. 7

a scheme according to Fig. 5 a second embodiment of a device according to the Fig. 1 or 2 .

Fig. 8

a scheme according to Fig. 5 a third embodiment of a device according to the Fig. 1 or 2 .

Fig. 9

a diagram of the time course of the temperature of the moist air in a working space of a dishwasher according to the Fig. 1 or 2 .

Fig. 10

a perspective view of a device for generating cold and heat of a device according to the Fig. 1 to 9 .

Fig. 11

a side perspective view of a dishwasher with a device according to Fig. 10 .

Fig. 12

the view XII in Fig. 11 .

Fig. 13

a diagram of the time course of the temperatures on a phase change material of a device according to the 10 to 12 .

Fig. 14

a principal rear view of another embodiment of a dishwasher with a device according to the invention and

Fig. 15

partly the view XV in Fig. 14 ,

Detailed description of the embodiments

In Fig. 1 a dishwashing machine 10 is shown, which contains a cubic working space 12. The working space 12 is bounded by two side walls 14, a rear wall 16, a bottom surface 18 and a top surface 20. The thus resulting front side 22 of the working space 12 is by means of a door, not shown, either to open or close.

At the working space 12 there is a device 24 which, among other things, is provided, in particular, for the possibility of drying the moist air produced in the working space 12 in the working space 12 under certain operating conditions. This drying takes place in particular at the end of a program sequence on the dishwasher 10, in which the dishes which are then located in the working space 12 are to be dried and completely freed from water residues.

In one embodiment, not shown, the device equipped with the device 24 is a tumble dryer, in which then by means of the device 24 located in the working space, moist air to be dehumidified during almost the entire period of operation.

The device 24 is designed with a heat exchanger or heat exchanger 26 and a control device 28, by means of which in particular the heat exchanger 26 can be flowed through with different types of fluid streams.

The heat exchanger 26 in this case has an upper opening 30 to the working space 12 toward, as well as a lower opening 32. The openings 30 and 32 are located in the in Fig. 1 illustrated embodiment, together with the heat exchanger 26 on one of the side walls 14. Alternatively, or in addition to this arrangement of the openings 30 and 32 may in Fig. 1 dashed lines 34 may be provided, which then produce a flow path between the rear wall 16 and the top surface 20 and / or the bottom surface 18 and the heat exchanger 26. These ports 34 may be coupled in the form of angled, flat channels to the heat exchanger 26 in multiple parts or be designed in one piece with this.

The Fig. 2 shows an embodiment of a heat exchanger 26, which is arranged on the outside of the rear wall 16 of the associated dishwasher 10. This arrangement has proved to be particularly advantageous in terms of the achieved drying result. The reason for the thus achieved, particularly good drying result is seen in that with the on the rear wall 16 arranged openings 30 and 32 results in a particularly favorable circulation flow of humid air within the cubic working space 12. This circulation flow is particularly good when the flow of air through the lower opening 32 out of the working chamber 12 out and into the heat exchanger 26 and the upper opening 30, the then dehumidified air from the heat exchanger 26 back into the working space 12. In this respect, it is important that the air on the front side 22 cools more strongly due to the poorer insulation and the seals on the door than on the side walls 14 and on the rear wall 16. Accordingly, the air that cools down decreases in the front in the working space 12 below and is then advantageously sucked back through the lower opening 32.

The heat exchanger 26 is, as in the 3 and 4 illustrated with a blown outer shell 36 and an internal, also blown line 38 designed. Alternatively, these blown parts can advantageously also be produced by means of an injection molding, thermoforming or other plastic molding process. The outer shell 36 has internal webs 40 and the line 38 is laid between these webs 40 serpentine or meandering, resulting in a particularly long flow path and thus a large heat transfer surface.

In the embodiment according to Fig. 3 is a single line 38 in the associated outer shell 36, whereas in the embodiment according to Fig. 4 In addition to the line 38, a second, also meandering line 42 is provided in the associated outer shell 36. This line 42 forms a second heat transfer circuit, so that with the heat exchanger 26 of this type, in particular a fluid located in the outer shell 36 can first be cooled by means of the line 38 and subsequently heated by means of the line 42.

At the bottom of such heat exchanger according to the 3 and 4 In each case, a condensate outlet or condensate separator 44 is formed, by means of which condensate collecting in the outer shell 36 can be collected.

In Fig. 5 the arrangement of a heat exchanger 26 to a working space 12 with the associated openings 30 and 32 is again illustrated. The Fig. 5 also shows that there the above-mentioned extraction of moist air into the heat exchanger 26 by means of a blower 46 (in the present case advantageously by means of a radial fan), which generates a negative pressure in the working space 12.

The Fig. 5 further shows that the inner conduit 38 of the heat exchanger 26 is preferably located farther from the inside of the outer shell 36 on the side facing the working space 12 than on the outwardly facing side. With this asymmetrical arrangement of the conduit 38 within the outer shell 36 is achieved that results in a favorable, low-resistance flow of moist air in the outer shell 36 and yet remains a large heat transfer surface. Furthermore, this forms a better insulation of the inner line 38 in the present case the rear wall 16 of the working space 12 (or in alternative embodiments with respect to one of the side walls 14). A good insulation against these walls of the working space 12 is therefore sought according to the invention, because the condensation of the water in the humid air according to the invention should take place specifically in the heat exchanger 26 and not on the walls of the working space 12. For this purpose, the heat exchanger 26 is furthermore preferably surrounded by a heat insulation layer. This thermal insulation also means that a fluid, which is located in the heat exchanger 26, holds its energy level for a long time and thereby also (residual) heat energy can be passed from one rinse to the next.

Finally, the illustrated Fig. 5 Also, a first embodiment of the remaining device 24, namely in particular the associated control device 28. Thus, the control device 28 according to Fig. 5 provided with a valve 48 to which the line 38 is connected. To this valve 48 performs a first line circuit 50, in which a pump 52 is arranged. The line circuit 50 is guided by a heat accumulator 54, which he can extract heat energy during operation of the pump 52 by a medium flowing in the conduit circuit. With The medium can be passed into the heat exchanger 26 with appropriate switching of the valve 48, this heat energy.

At the valve 48, a line circuit 56 is further connected, through which a pump 58 can promote a cold leading (or heat dissipating) medium. The medium is guided by the line circuit 56 through a cold storage 60.

Between the heat storage 54 and the cold storage 60 is a device 62 for generating cold and heat, which is designed in this case in particular by means of a Peltier element. As an alternative to a Peltier element, the device 62 may be formed in a conventional manner with a compressor / expansion circuit.

In the Fig. 6 a variant embodiment of a device 24 is shown, which is also designed with a cold storage 60 and a heat storage 54. However, the heat accumulator 54 is not coupled via a line circuit for a fluid, in particular a liquid heat transfer medium with the heat exchanger 26, but via an air line 64 from the environment of the dishwasher 10 (as shown) from in the heat storage 54 or (not shown) from the working space 12 out into the heat storage 54. The air line 64 is then further passed through the heat storage 54 and into the heat exchanger 26, wherein a blower 66 arranged there in the air line 64 can force this air flow. The blower 66 which has already been described can also be used as blower 66 in that the air line 64 as well as the lower opening 32 are coupled to a valve (in particular the valve 48). The valve can then switch the corresponding conduction paths in such a way that air from the environment or from the working space 12 is conveyed through the heat accumulator 54, thereby being heated and then conveyed in particular into the outer sheath 36 of the heat exchanger 26. The case dissipated from the heat storage 54 heat can be used in this way, in particular in associated program steps, the air in the working space 12 to heat or water, especially fresh water preheat or heat, which may then be located in the line 38 of the heat exchanger 26.

As an alternative to supplying the warm air from the heat accumulator 54 by means of a blower 66 into the heat exchanger 26, this air can also be fed directly into the working space 12 in an embodiment not shown. This can also increase the air temperature in the working space 12 and in this way the capacity for water vapor can be increased.

The Fig. 7 shows an embodiment of a device 24, in which to the heat accumulator 54 also a line circuit 50 is provided for heat dissipation with a pump 52 disposed therein. However, this line circuit 50 is connected by means of its own valve 67 to the inner, upper line 42 of the heat exchanger 26. At the same time located in the heat exchanger 26, an inner lower line 38 which is selectively coupled by a valve 48 with the cold storage 60 in a fluid-conducting manner. With the heat accumulator 54 and cold accumulator 60 thus coupled to the heat exchanger 26, moist air can be cooled from the working space 12 in the heat exchanger 26 in appropriate program steps of the dishwasher 10, in particular at the lower line 38, and in this way the steam present therein can be condensed out. The air can subsequently be reheated to line 42 before being returned to the working space 12.

In the area of the line 42 located in the heat exchanger 26, in another exemplary embodiment (not illustrated in more detail) a container with a reversible, dehydratable material, in particular zeolite, is arranged through which moist air can be passed from the working space 12 by means of the blower 46. This passing is preferably carried out after a large part of the water vapor from the moist air has already been precipitated by cooling on the line 38. The remaining water vapor is essentially taken up by the zeolite. For desorption of the zeolite can then in a subsequent program step this area of the heat exchanger 26 is heated by means of the line 42 and the heat storage 54 connected thereto and in this way the water is separated from the zeolite again, so that the reversible, dehydratable material for the next operation of dehumidifying the air from the working space 12 again is prepared.

In the Fig. 8 the device 24 is illustrated in a variant embodiment, in which on the bottom surface 18 of the working space 12, a sump 68 is formed with a line circuit 70 and a pump 72 arranged therein. The pump 72 may alternatively be replaced by one of the pumps 52 or 58 with appropriate circuit. The line circuit 70 may be connected to a water drain located in the sump 68 and / or to a water softening regenerator (not shown in more detail). In the present case, the line circuit 70 can be coupled to the outer shell 36 of the heat exchanger 26 in a fluid-conducting manner. Alternatively, the line circuit 70 may be coupled to the line 38 or the line 42 in the interior of the heat exchanger 26, for example, characterized in that it is guided to the valve 48, which is then switched accordingly. With the conduit circuit 70, water which flows out of the working space 12 can be temporarily stored in the heat exchanger 26 and, in particular, its residual heat energy can be utilized. Furthermore, desired temperature levels can be adjusted at the regeneration device by supplying it in particular with cold from the cold storage 60 or heat from the heat storage 54. In this case, the line coupling via the valve 48 can be used.

With the device 24 of this type, in operation of the associated dishwasher 10 in the working space 12, in particular, a Fig. 9 illustrated temperature profile controlled. Initially, the temperature is raised from about 20 degrees room temperature by introducing heated water to about 50 ° C. As water fresh water or previously remaining from the last rinse residual water can be used, which has been cached in particular as explained above in the heat exchanger 26. The water can be pre-tempered by means of the heat accumulator 54 or kept at temperature. This results in comparison to conventional devices, a first potential savings in energy and fresh or raw water.

In the subsequent wash cycle, the water and thus also the air in the working space 12 cools substantially linearly to a temperature of about 40 to 45 ° C. The water is then pumped off, whereby the temperature in the working space 12 continues to e.g. about 35 ° C drops. This temperature is adjusted in particular by the fact that subsequently fresh water is supplied again for a rinsing process. In the present case, it is provided that the last part of water from the first rinse cycle stored in the heat exchanger 26 and this water can be used in the subsequent rinse cycle to preheat the fresh water.

In conventional dishwashers 10 (this is indicated by a solid curve 74 in FIG Fig. 9 illustrated) heated during the rinsing process, the working space 12 with the humid air therein to a temperature of about 68 degrees Celsius (° C). This temperature is particularly necessary if a particularly good drying result is to be achieved in a subsequent drying cycle.

However, this is not necessary with the device 24 according to the invention. On the contrary, the device 24 makes it possible for the moist air in the working space 12 to be heated only to a temperature between 40 ° C. and 50 ° C., in particular between 48 ° C. and 42 ° C. (see the dashed curve 76 in FIG Fig. 9 ). Subsequently, namely with the fan 46, a circulation of moist air through the heat exchanger 26. At the same time in this water in the line 38 with a temperature of less than about 20 ° C, preferably between 15 ° C and 5 ° C, provided. The water may advantageously be fresh water that has previously been passed through the cold storage 60.

With the water so cold in the heat exchanger 26 of the moist air from the working space 12 of the steam is precipitated so well that, as experiments have shown, excellent drying results. At the same time due to the low temperature of the working space 12 for the rinse and drying cycle very little energy is required, which in comparison to known devices, a significant energy saving can be achieved. Experiments have shown that consistently at least one energy saving of more than 200 watt hours (Wh) per wash program and thus more than about 50 kilowatt hours (kWh) per device and year can be achieved. In addition, there is a considerable potential for saving water. Finally, with the procedure according to the invention, the cycle time for the drying as a whole can be shortened, whereby a shortening of approximately 25 minutes (min) can result for the associated washing program. Overall, this has contributed significantly to the protection of the environment.

In the procedure according to the invention, the system is also closed, so that no outlet, for example in the base area of the device, is necessary. The system is therefore in comparison to known systems in terms of noise and odor emissions advantage.

In the 10 to 12 an embodiment of a device 24 is illustrated in which the cold storage 60 is formed by means of an ice storage. The ice storage comprises a single or multi-walled, in particular double-walled housing 78, on which a single or multiple Peltier element is arranged as a device 62 for generating cold and heat. The Peltier element generates in the housing 78 as a latent cold storage an ice core 80, which can be flowed around by a cooling medium, in the present case water. To the housing 78 to the passage of the water to two ports 82 are formed.

On the warm side of the Peltier element several heat pipes or heat pipes 83 or other heat-dissipating elements are arranged, in which means Phase transformation heat energy is transported away from the Peltier element. The heat energy is conducted to a heat accumulator 54, which in the present case is filled with a phase change material (PCM, phase change material). This material also stores large amounts of heat by undergoing a phase transformation. The phase transformation may be solid-solid, solid-liquid, liquid-gaseous or solid-gaseous. The transformation enthalpy of the phase transformation is very low. Preferably, a phase change material is used, in which a (partial) melting process is used as a phase transformation. Before and after the phase transformation, the thermal energy is sensitively stored according to the specific heat capacity of the material. During the phase transformation, however, the temperature of the material does not change, the heat energy is "hidden" or stored latent. In the present case, preference is given to materials which, in addition to a high enthalpy of fusion, also have a high heat capacity, in particular inorganic salts and salt hydrates, their eutectic mixtures and eutectic water-salt solutions, as well as paraffins or sugar alcohols. Further, these materials are flowable in the form of a slurry.

The processes of the phase changes are in the diagram of Fig. 13 1, which shows the course of the temperature of the phase material on the basis of a solid curve 86 and the course of the temperature of the associated Peltier heater with the aid of a dashed curve 88. Two plateaus 90 and 92 in the curve 88 show those points where the phase change material melts (plateau 90) and again (at least partially) solidifies or freezes (plateau 92).

The heat accumulator 54 of this type can be cooled by an air flow through an air line 64 by means of a blower 66, and its heat energy can be dissipated in this way. The air line 64 can be guided directly into the working space 12. The FIGS. 11 and 12 further show how the lines in the bottom of the bottom surface 18 from the sump 68 and a regenerating device 84 arranged there are guided to the valves 48 and / or 67.

In the FIGS. 14 and 15 an embodiment of a device is shown, in which the heat exchanger 26 is also disposed on the rear wall 16 of the working space 12. The heat exchanger 26 can be cooled by the line circuit 56 with an associated pump 58 from a cold storage 60 out. Furthermore, moist air can be conveyed through the heat exchanger 26 by means of the blower 66 out of the working space 12, the air being sucked through the upper opening 30 into the heat exchanger 26. At the lower opening 32 is located in the air line 64 such a further heat exchanger 94, which is connected via heat pipes or heat pipes 96 with the heat storage 54. In the heat accumulator 54 is thereby a phase change material as a storage medium that can be promoted by a pump 97 through a conduit circuit 98 to the hot side of the associated Peltier element.

With the heat exchanger 94, the air blown into the working space 12 by means of the blower 66 can thus be directly heated and thus prepared for a further absorption of water vapor.

LIST OF REFERENCE NUMBERS

10

dishwasher

12

cubic workspace

14

Side wall

16

rear wall

18

floor area

20

cover surface

22

front

24

contraption

26

Heat exchanger

28

control device

30

upper opening

32

lower opening

34

alternative connections

36

outer shell

38

management

40

web

42

management

44

condensate

46

fan

48

Valve

50

Line circuit (heat)

52

pump

54

heat storage

56

Line circuit (cold)

58

pump

60

cold storage

62

Device for generating cold and heat

64

air line

66

fan

67

Valve

68

swamp

70

Piping circuit

72

pump

74

Curve

76

Curve

78

casing

80

ice core

82

connection

83

Heat pipe

84

regenerating

86

Curve

88

Curve

90

plateau

92

plateau

94

additional heat exchanger

96

Heat pipe

97

pump

98

Conduit circuit

Claims (8)

1. Method for drying humid air from a working space (12) of a water-carrying machine, in particular a dishwashing machine (10), said method comprising the following steps:

   - provision of the humid air in the working space (12) at a temperature of between 40°C and 50°C;

   - provision of a cooling medium in a heat-exchanger (26) at a temperature of below 20°C;

   - conduction of the humid air, which has been temperature-controlled in this way, out of the working space (12) through the heat-exchanger (26),

   wherein the cooling medium is cooled before it is provided in the heat-exchanger (26) and said cooling medium is cooled by means of a circuit (56) at a cold reservoir (60).
2. Method according to Claim 1,
   in which suitably temperature-controlled fresh water is provided in the heat-exchanger (26) as the cooling medium.
3. Method according to Claim 1 or 2,
   in which the cold reservoir (60) is constituted by means of an ice reservoir (60; 80).
4. Method according to one of Claims 1 to 3,
   in which a heating medium (42; 94) is also provided in the heat-exchanger (26), wherein the humid air from the working space (12) is conducted within said heat-exchanger (26), in particular, first past the cooling medium and then past the heating medium.
5. Device for drying humid air from a working space (12) of a water-carrying machine, in particular a dishwashing machine (10), which device is adapted to:

   - provide the humid air in the working space (12) at a temperature of between 40°C and 50°C;

   - provide a cooling medium in a heat-exchanger (26) at a temperature of below 20°C; and

   - to conduct the humid air, which has been temperature-controlled in this way, out of the working space (12) through the heat-exchanger (26); and also

   - to cool the cooling medium before it is provided in the heat-exchanger (26) and

   - to cool the cooling medium by means of a circuit (56) at a cold reservoir (60; 80).
6. Device according to Claim 5,
   which is adapted to provide suitably temperature-controlled fresh water as the cooling medium in the heat-exchanger (26).
7. Device according to Claim 5 or 6,
   in which the cold reservoir is constituted by means of an ice reservoir (60; 80).
8. Device according to one of Claims 5 to 7,
   which is adapted to also provide a heating medium (42; 94) in the heat-exchanger (26), wherein the humid air can be conducted within the heat-exchanger (26), in particular, first past the cooling medium and then past the heating medium.

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