WO2001096794A1

WO2001096794A1 - Method and device for air conditioning using waste heat

Info

Publication number: WO2001096794A1
Application number: PCT/PL2001/000033
Authority: WO
Inventors: Bogusław ZAKRZEWSKI
Original assignee: Zakrzewski Boguslaw
Priority date: 2000-06-15
Filing date: 2001-04-13
Publication date: 2001-12-20
Also published as: AU2001252801A1; PL191519B1; PL340843A1

Abstract

Conditioned space (P) is connected to main ventilation duct (KG) and auxiliary ducts (K1, K2) also connected to the main duct. Duct (K1) is connected via first heat exchanger (W1), and duct (K2) is connected via second heat exchanger (W2). Between the heat exchangers is split damper (9) connect to system for automatic control and regulation (17), and auxiliary ducts (K1, K2) are connected to conditioned space (P) via inner air dampers (13, 10) and to outdoor space by outer air dampers (12, 11). Inner air damper (14) is positioned between main duct (KG) and conditioned space (P). The dampers are controlled by system for automatic and regulation (17).

Description

Method and device for air conditioning using waste

The present invention relates to a method for regulation of air parameters in conditioned spaces, especially in stores of products sensitive to climatic conditions, system for regulation of air parameters in conditioned spaces, especially in stores of products sensitive to climatic conditions and apparatus for regulation of air parameters in conditioned spaces, especially in stores of products sensitive to climatic conditions.

A method and system for air-conditioning of frozen food packing compartments in cold stores with cooling, heating and dehumidifying air in layered heat exchangers filled with refrigerant is known from description of the Patent No PL 157065. The method is characterized in simultaneous action of two separate recirculative air circulations. The first circulation takes place in the upper part of the conditioned space and consists in cooling air in summer period and heating air in winter period to required temperature using fan heat exchangers. The second circulation takes place in the lower part of the conditioned space and consists in dehumidifying moist air. The air from the conditioned space is passed to the dehumidification unit where it is cooled to remove moisture. The dehumidified air is heated to required temperature and passed to the conditioned space containing frozen food. The essence of the system consists in that heat exchangers connected to the cooling arrangement are situated under the ceiling in opposite corners of the compartment. Intake duct of dehumidified air, connected to the fan and the dehumidification unit with built-in isolated heat exchanger blocked with tray and another exchanger and suction duct with inlet openings, is situated over the floor on the opposite side to outlet openings of the air intake duct. Both exchangers of the dehumidification system and the tray are connected to refrigeration arrangement.

The device for continuos dehumidifying air with housing formed by ventilation duct is described in Patent No PL 157051. Surface cooler with condensate tank, cooling compressor, air-cooled condenser and fan are situated in the ventilation duct. The method of continuos dehumidifying air consists in that in the first stage stream of outdoor air passes through the cooler. The cooler cools the air to temperature lower than dewpoint of outdoor air and, as a result, portion of moisture from dehumidified air is released on the cooler surface. In the second stage stream of dehumidified air, being in saturated state, passes through the heater and is heated to temperature greater than dewpoint. The device has neither a possibility to decrease air temperature below ambient temperature nor keep air temperature at required level. Neither independent cooling air nor independent heating is possible in this solution with applied unidirectional air circulation. The process of dehumidifying air is known which consists in condensation of moisture on air cooler walls being a part of cooling set. The process is accompanied by increase of relative humidity almost to 100%. Reduction of moisture of dehumidified air requires supply of thermal energy from outside. In such systems cooler surface temperature is normally kept above

0 degrees C (32 degrees F). It is caused by risk of frosting of the surface in low temperature. The process of frosting and defrosting of the surface complicates operation of device and increases energy consumption. In such systems a method is applied, for example, for defrosting of evaporator consisting in replacement of functions of heat exchangers; evaporator becomes condenser and condenser becomes evaporator. This is achieved by reversing refrigerant circulation using appropriate control valves, for example multi-way valves. It is an example of application of the known heat pump circulation. The cooling device working as a heat pump lacks thermal power, especially when ambient temperature is low. Defrosting time is then long.

This is the reason why electric heaters are commonly applied to defrost coolers. It complicates the system and increases the operational costs of cooling device or heat pump. Additionally, amount of heat emitted to the conditioned space is considerable. Regular operation of cooling device or heat pump is interrupted when the evaporator is defrosted.

The known air-conditioning system with air parameter control described in handbook "Heating and air-conditioning", Recknagel.Sprenger.Honmann.Scliramek EWFE, Gdansk, 1994, p. 1769 contains a cooling system composed of the compressor connected to heat exchangers, evaporator and condenser via the pipeline. The system is equipped with an expansion valve, control valves, air fans and a device for automatic circulation adjustment. Air circulation in conditioned space is forced; fan impels air stream to the ventilation duct and evaporator situated there. Each exchanger can operate as air cooler or condenser, after switching over the multi-way valve each exchanger can also operate as a condenser heating the conditioned space.

The method according to the invention, using compressor cooling circulation and air circulation through the ventilation ducts equipped with dampers consists in that in the air cooling cycle in air conditioned space, indoor air is passed to the first heat exchanger of the cooling system being an evaporator, and air outdoor is passed to the second heat exchanger being a condenser. When the parameter monitored at the evaporator obtains required value, direction of circulation is reversed so that the first heat exchanger is a condenser and the second one is an evaporator and the indoor air fan and outdoor air fan are switched off. Indoor air is passed to the evaporator and further back to the conditioned space while outdoor air is passed to the condenser. When temperature of the evaporator surface is near its ambient temperature, the conditioned space air fan is switched on, and the fan forcing air stream around the condenser is switched on when temperature of the condenser surface is near its ambient temperature. In the cycle of heating air, indoor air is supplied to the condenser and the air is passed back to the conditioned space while outdoor air is supplied to the evaporator. After the parameter monitored at the condenser obtains required value, direction of circulation is reversed so that the first heat exchanger is again an evaporator and the second one is again a condenser, air stream is shut off to the conditioned space and outdoor air is supplied to the evaporator and condenser.

The cycle of dehumidifying air is performed by cooling and heating air. Dependant on the requirements, either continuous dehumidifying air or alternately dehumidifying and heating can be carried out. In the case of continuous dehumidifying air, indoor air is supplied through the first ventilation duct to the first heat exchanger (evaporator), and indoor air is supplied to the another heat exchanger (condenser). After the monitored parameter at the evaporator obtains required value and/or when temperature in the conditioned space obtains required value, indoor air is supplied to the condenser and back to the conditioned space, and outdoor air is supplied to evaporator. After temperature in the conditioned space obtains required value, the direction of air circulation is reversed. Again indoor air is supplied to the evaporator and outdoor air is supplied to the condenser. The air circulation is repeated many times until required humidity and/or temperature in conditioned space is obtained. When air is continuously dehumidified, indoor air is supplied through the first ventilation duct to the first heat exchanger (evaporator), while to the second heat exchanger (condenser) indoor air is supplied through another ventilation duct (inner duct). After required value of the monitored parameter is obtained at the evaporator, defrosting cycle is realized (outdoor air is now supplied to the both heat exchangers) and/or when required value of the monitored temperature in the conditioned space is obtained, outdoor air is periodically supplied to the condenser. When the temperature decreases to the minimal threshold value, indoor air is again supplied to the condenser. When required humidity of indoor air is obtained the cycle is terminated. The method can be applied either if the temperature close to the heat exchanger surface is above 0 degrees C (32 degrees F) - condensate comes out on the surface, or if the temperature is below 0 degrees C (32 degrees F) - then frost is deposited. The arrangement has much greater efficiency working in the "deep" dehumidification mode - when dewpoint is less than 0 degrees C (?? degrees F) - than the already-known dehumidification systems working in the temperature of evaporator surface below 0 degrees C (32 degrees F) in frosting conditions. Using the method it is possible to obtain significantly less partial pressures of dehumidified air in conditioned space maintaining large energetic efficiency. Beneficially, in the heating cycle warm air from additional source (marine power plant) is supplied to the evaporator. It applies to conditions when outdoor air temperature - low temperature heat source is small. Waste heat of marine power plant ventilation system can be applied. Beneficially, the monitored parameter is at the evaporator is time of evaporator operation. Beneficially, the parameter monitored at the evaporator is thickness of frost layer on the evaporator surface. Beneficially, the parameter monitored at the evaporator is difference of the temperature of air in the conditioned space and temperature of the frost surface on the evaporator.

Beneficially, the parameter monitored at the evaporator is difference of the temperature of saturation point in the conditioned space and temperature of the frost surface on the evaporator.

Beneficially, the parameter monitored at the evaporator is mass of frost. Beneficially, the parameter monitored at the evaporator (1,1') is difference of pressures of refrigerant in front of and behind the evaporator. Beneficially, the parameter monitored at the evaporator is difference of temperatures of air in front of and behind the evaporator. Beneficially, the parameter monitored at he evaporator is temperature of air in the conditioned space. Beneficially, the parameter monitored at the evaporator is relative humidity of air in the conditioned space.

Beneficially, the parameter monitored at the evaporator is absolute humidity of air in the conditioned space.

A system for regulation of air parameters in conditioned space, composed of compressor cooling system and system for air circulation containing ventilation ducts equipped with dampers and fans according to the invention is characterized in that conditioned space is connected to main ventilation duct and two auxiliary ducts connected to the main duct. The first auxiliary duct is connected via first heat exchanger, second auxiliary duct is connected to the main duct via second heat exchanger. Between the heat exchangers is positioned split damper com ected to system for automatic control and regulation. Auxiliary ducts are connected to conditioned space via inner air dampers and to outdoor space by outer air dampers. Beneficially, first auxiliary duct and second auxiliary duct are connected to third auxiliary duct which is connected to the conditioned space. Beneficially, the conditioned space is connected to the main duct via inner duct and fourth imier air damper, and the main duct is connected to outdoor space via third outer damper. Beneficially, the main duct is connected via fourth damper to supply air duct which is connected to low-temperature waste heat source contained in air, and the main duct is connected to outdoor space via the third outer air damper.

Beneficially, split damper is a three-position sequential air damper which can be pivoted by 45°, where in first position "A" the first auxiliary ventilation duct is connected to the conditioned space, and in second position "B" the second auxiliary ventilation duct is connected to the conditioned space, and in null position "0" both ventilation ducts are connected to outdoor space.

Apparatus for regulation of air parameters in conditioned spaces, equipped with cooling arrangement including compressor, ventilation ducts with dampers and fans according to the invention is characterized in that conditioned space is connected to main ventilation duct and first and second auxiliary ducts. The main duct connects the conditioned space to outdoor space. The first heat exchanger of cooling arrangement is situated between the main duct and first auxiliary duct, and the second heat exchanger is situated between main duct (KG) and second auxiliary duct. Split damper is situated between the heat exchangers, connected to system for automatic control and regulation. Inner dampers are situated on the walls of the ducts on the side of the conditioned space, and outer dampers are situated on the outer walls of the ducts on the side of conditioned space. Outer and inner air fans are connected to the main duct.

Beneficially, split damper in the main duct is three-position sequential damper which can be pivoted by 45°, where in first position "A" first auxiliary ventilation duct is connected to the conditioned space, and in second position "B" second auxiliary ventilation duct is connected to the conditioned space, and in null position "0" both heat exchangers are connected to outdoor space. Beneficially, first and second heat exchangers are situated parallelly and opposite to each other. Beneficially, outer air fan is situated at inlet of main duct, and inner air fan is situated at outlet of the main duct to the conditioned space.

Many energetic benefits can be obtained applying the method and system due to the invention in devices working according to the refrigeration cycle. The method eliminates electric heaters for defrosting evaporators and electric energy for powering compressor decreases by 50% (COP:

2.5-4.0 in known applications and 5.0-10.0 in application according to the invention).

Unexpectedly it turned out that by switching ducts controlling air stream it is possible to use waste heat accumulated in another compartment, for example from marine power plant or outdoor heat, to decrease consumption of electric energy to defrost evaporator of heat pump.

Simultaneously both heat exchangers: upper and lower heat source operate in similar temperatures what ensures maximal energetic efficiency of the heat pump. This implementation gives a possibility of stabilization of air temperature in the conditioned space with accuracy unavailable in other systems, with very low energy consumption and using waste energy.

The invention is explained in details using examples of implementation and in the figures. Fig. 1 presents schematically the system according to the invention in the mode of cooling air.

Continuous lines and arrows indicate directions of air streams and direction of refrigerant stream.

Dashed line indicate position of four- way valves when direction of circulation is reversed. Fig. 2 presents a fragment of the system according to the invention in the defrosting mode during operation as a cooling arrangement. Fig. 3 presents a scheme of the system in the heating air mode. Continuous lines and arrows indicate directions of air streams and direction of refrigerant stream. Dashed line indicate position of four-way valves when the direction of circulation is reversed. Fig. 4 presents a fragment of the system in the mode of heating air and defrosting. Continuous lines and arrows indicate directions of air streams. Fig. 5 presents schematically a modification of the system according to the invention in the mode of cooling air. Fig. 6 presents schematically a modification of the system according to the invention in the mode of heating air using waste heat. Fig. 7 presents schematically a modification of the system according to the invention in the mode of heating air using additional source of outdoor air. Fig. 8 presents schematically a modification of the system in the cycle of dehumidifying air in the conditioned space.

Example I

The system for regulation of air parameters in conditioned space contains compressor 3. The press pipeline of the compressor is connected to the inlet connector pipe of the first four-way valve Zl, and the remaining connector pipes of the valve are connected to the heat exchangers: first heat exchanger Wl and second heat exchanger W2, and tank 4 with regeneration exchanger

4a. Tank 4 is connected to suction pipeline of compressor 3. The inlet of regeneration exchanger

4a is connected to outlet connector pipe of second four-way boiling valve Z2. The outlet is connected to inlet connector pipe of valve Z2 via dehydrating filter 5 and expansion valve 6.

Remaining two connector pipes of four- way boiling valve Z2 are connected to another ends of coils of first heat exchanger Wl and second heat exchanger W2. Valves Zl and Z2 are in first position I in which the direction of circulation is such that first heat exchanger Wl is evaporator

1 and second heat exchanger W2 is condenser 2. Conditioned space (P) is connected to three ventilation ducts: main ventilation duct KG and adjoin auxiliary ducts Kl, K2. In first auxiliary duct Kl situated is first heat exchanger Wl, and in second auxiliary duct K2 situated is second heat exchanger W2.

First outer air damper is situated on the outer wall of first auxiliary duct Kl, and first heat exchanger Wl is situated on the wall common with main ventilation duct KG. First heat exchanger Wl is evaporator 1, and after reversal of direction of cooling circulation it becomes condenser 2'. Opposite to first heat exchanger Wl, on the other side of main duct KG situated is in second duct K2 second heat exchanger W2. Second heat exchanger W2 is condenser 2, and after reversal of direction of cooling circulation it becomes evaporator 1'. Second inner air damper 13 is situated at the outlet of duct Kl to conditioned space P, and second outdoor air 12 is situated on the outer wall of duct Kl. Damper 12 controls air stream from outdoor space to duct Kl . Second outer air damper 11 is situated on the wall of duct K2, and first im er air damper

10 is situated at the outlet of duct K2 to conditioned space P. In main duct KG, between heat exchangers Wl and W2 is three-position sequential split damper 9 connected to system for automatic control and regulation (17), controlled by microprocessor. Depending on requirement, split damper is pivoted by 45° in either direction or is the null position, paralelly to the walls of main duct KG. In first position "A" of split damper 9 first auxiliary ventilation duct Kl is connected to conditioned space P, and in second position "B" second auxiliary ventilation duct

(K2) is connected to conditioned space (P), and in null position "0" both ventilation ducts

(K1,K2) are connected to outdoor space. Outdoor air fan 7 is situated at air inlet to main duct

KG, and indoor air fan 8 is situated at the outlet of the main duct to conditioned space P. Third inner damper 14 is situated in main duct KG, opening or shutting off air stream to conditioned space P. In the cooling cycle fan 8 impels air stream to conditioned space P. The air flows to first auxiliary duct through open damper 13. In the duct the air flows through the first heat exchanger which is evaporator 1 and further flows to main duct KG. Evaporator 1 cools the air.

Simultaneously split damper 9 is in position A and shuts off outdoor air to main duct KG, damper 14 is open, and inner damper 14 and outer damper 12 are closed. Cooled air is impelled by fan 8 from main duct KG back to conditioned space P. Simultaneously outdoor air, impelled by fan 7, passes through condenser 2 to second auxiliary duct K2. Condenser 2 heats outdoor air which flows through open second outdoor air damper 11 back to outdoor space. After required temperature of air in conditioned space P is obtained the circulation operates in regular mode controlled by temperature of air in conditioned space P.

In cycle of defrosting evaporator 1, presented in Fig. 1, when required low temperature in conditioned space P starts to increase and obtains the maximum threshold value or when on the evaporator surface frost layer is deposited, four- way valves Zl, Z2 are switched to second position II by electronic control system 17 and the direction of circulation of refrigerant is reversed in such a way that first heat exchanger Wl becomes condenser 2' in the new circulation and second heat exchanger which was a condenser becomes evaporator 1'. Simultaneously split damper 9 is pivoted to second position B and damper 13 is closed. After reversing the circulation and switching the dampers, cool air from conditioned space P is supplied with delay to second duct K2 through open damper 10. Evaporator (so far condenser, which surface shortly after switching obtains ambient temperature) cools the air which passes through main duct KG and damper 14 back to conditioned space P. Simultaneously second outer damper 12 is open and outdoor air passes through condenser 2' and damper 12 outdoors. In the time when heat exchangers Wl and W2 are switched, fans 7 and 8 are turned off. Directly after the circulation is reversed, fans 7 and 8 are switched off. Fan 8 impelling air stream to conditioned space P is switched on again when the temperature of the surface of evaporator 1 ' is near its ambient temperature. Fan 7 is switched on when temperature of the evaporator surface is near its ambient temperature what happens with large delay. The arrangement continues operation in cycle of cooling air in conditioned space P.

In cycle of heating air in conditioned space P, presented in Fig. 3, damper 13 is opened, and split damper is pivoted to position A shutting off outdoor air stream to conditioned space P. Fan 8 impels air flow to conditioned space P. The air passes through damper 13 to duct Kl. Hot condenser 2' heats the air, which passes through duct KG and open damper 14 and is further impelled by fan 8 to conditioned space P. Simultaneously outdoor air is impelled by fan 7 to evaporator 1 ' and further to duct K2 and flows outdoor through open damper 11.

In cycle of defrosting of evaporator 1', presented in Fig. 4 four- way valves Zl and Z2 are placed in first position I. The direction of circulation is reversed and first heat exchanger Wl becomes evaporator 1 again and second heat exchanger becomes condenser 2 again. Fan 8 is switched off.

Simultaneously split damper 9 is pivoted from position A to position 0 and changed are positions of dampers 10,11,12,13,14. Now dampers 10,13,14 are closed and dampers 11,12 are open.

Outdoor air flows through condenser 2 increasing its surface temperature, passes to duct K2 and flows outdoor through open damper 11. Another stream of warm air flows through evaporator 1.

Simultaneously both heat exchangers; evaporator 1 and condenser 2 operate in the same temperature what results in maximal energetic efficiency of the system.

In the cycle of dehumidification, air from conditioned space P is supplied through duct Kl to first heat exchanger Wl (evaporator 1), and to second heat exchanger (condenser 2) outdoor air is supplied through main duct KG. When the parameter monitored at evaporator 1 obtains required value and/or when temperature t in conditioned space P obtains required value, position of dampers 9,13,12,10,11 is changed and air from the conditioned space to condenser 2 and back to the conditioned space, and outdoor air is supplied to evaporator 1. After temperature in conditioned space P obtains required value, the direction of circulation is reversed and air from conditioned space P is supplied to evaporator 1 again, and outdoor air is supplied to condenser 2.

Such circulation is repeated many times until required humidity eg and/or temperature t in conditioned space P is obtained.

Example II

System similar to example I which is presented in Fig. 1. Difference is, as shown in Fig. 5, that first auxiliary duct Kl and second auxiliary duct K2 are connected to conditioned space P via third auxiliary duct K3.

Example III

System similar to example I which is presented in Fig. 3. Difference is, as shown in Fig. 6, that main duct KG and second auxiliary duct K2 are connected to additional supply duct KZ via fourth inner damper 15. Duct KZ is connected to compartment S which is a source of waste heat contained in air, for instance marine power plant. Warm air from compartment S passes through main duct KG to heat exchanger W2 which is evaporator 1 ' in this circulation. In supply duct KZ situated is third outer damper 16 controlling air stream supplied to main duct KG. Split damper 9 is then pivoted to position A, connecting first auxiliary duct Kl to conditioned space P.

Circulation is supplied, depending on thermal conditions, either with waste heat from supply duct KZ or, if thermal parameters of outdoor air are higher, damper 16 can be open and damper

15 - closed. When heat exchangers are switched over, fan 8 is turned off. Simultaneously, after heat exchangers are switched, fan 7 impels air stream to both ducts K1,K2, and the fan is switched to impel air stream to one of the heat exchangers when the surface of evaporator 1 ' is defrosted (temperature of its surface increases to value near the temperature of conditioned space

P). In this time the system is not active if temperature of air supplied by duct KZ from compartment S is large enough. If the temperature is low, the system is active during defrosting with identical temperature in both heat exchangers, with maximal efficiency. Split damper is positioned to "0", dampers 13, 14 are closed, and dampers 11, 12 are opened. Next split damper

9 is pivoted from "0" to "B" position, fan 8 is turned on impelling air stream to condenser 1', dampers 10, 14 are opened, and damper 11, which was open for defrosting, is closed.

Example IV

System similar to example III. Difference is, as shown in Fig. 7, that auxiliary ducts Kl and K2 are connected to conditioned space P via third auxiliary duct K3.

Example V

System similar to example I. Difference is, as shown in Fig. 8, that first auxiliary duct Kl is connected directly to conditioned space P via damper 13, second auxiliary duct K2 is connected directly to conditioned space P via damper 10, and main duct KG to conditioned space P via auxiliary internal duct KW and fourth damper 15. Main duct is connected via third damper 16 to outdoor space. In this system cycle of dehumidifying air is realized in constant temperature in conditioned space P, with steam condensating or frost deposited on the surface. Air from conditioned space P is supplied through fourth internal damper 15 to main duct and further the air stream is impelled by fan 7 to condenser 2. The air is heated and flows back to conditioned space P. Split damper 9 is in position "A".

It is also possible to dehumidify air cyclically. In cycle of dehumidifying air, air from conditioned space P is supplied through first duct Kl to first heat exchanger Wl which is evaporator 1, and to second heat exchanger W2 which is condenser. Air is supplied from the conditioned space through internal duct KW. After the parameter monitored at evaporator 1 obtains required value, cycle of defrosting is carried out and/or when temperature in conditioned space P obtains required value, outdoor air is periodically supplied to the condenser.

When the temperature decreases to the minimal threshold value, indoor air is again supplied to the condenser. When required humidity φ of air in conditioned space P is obtained the cycle is terminated.

In this system it is possible to stabilize temperature of air in the conditioned space with accuracy unavailable applying other systems, with very small energy consumption and using waste heat.

Claims

Patent claims

1. A method of regulation of air parameters in conditioned spaces, especially in stores of products sensitive to climatic conditions, in which forced air circulation is applied, air is supplied by fans through ventilation ducts equipped with dampers and connected to conditioned space, parameters are regulated by periodic cooling, dehumidifying and heating air using compressor cooling system equipped with heat exchangers, control valves and expansion valve, evaporator cools the air stream and condenser heats the air stream, direction of circulation of the refrigerant is reversed using control valves and automatic regulation and control systems, the method characterised in that in the cycle of cooling air

(1) supplying indoor air to first heat exchanger (Wl) which is evaporator (1) and supplying outdoor air to second heat exchanger (W2) which is condenser (2);

(2) reversing cooling circulation after the monitored parameter at evaporator (1) obtains required value in such a way that first heat exchanger (Wl) becomes condenser (2j , and second heat exchanger (W2) becomes evaporator (T);

(3) switching off indoor air fan (8) and outdoor air fan (7);

(4) directing indoor air from conditioned space (P) to evaporator (1') and further back to conditioned space (P) and directing outdoor air to condenser (2');

(5) switching on indoor air fan (8) after temperature the evaporator (1 ') surface is near its ambient temperature and switching outdoor air fan (7) after temperature at the surface of evaporator (2') is near its ambient temperature; in the cycle of heating air

(6) directing indoor air from conditioned space (P) to condenser (2') and back to conditioned space (P) and directing outdoor air to evaporator (1');

(7) reversing circulation after the monitored parameter at evaporator (1) obtains required value in such a way that first heat exchanger (Wl) becomes evaporator (1) again, and second heat

• exchanger (W2) becomes condenser (2) again;

(8) shutting off the air stream to the conditioned space (P);

(9) supplying outdoor air to evaporator (1) and condenser (2);

(10) dehumidifying air in conditioned space (P) in the way of cooling and heating air.

2. The method of claim 1, wherein in the cycle of heating air, warm air from a waste heat source (S) contained in air is supplied through supply duct (KZ) to evaporator, independent which of heat exchangers Wl and W2 is an evaporator.

3. The method of claim 1, characterised in that, in the cycle of dehumidifying air, air from conditioned space (P) is supplied to first heat exchanger (Wl) which is evaporator (1), and outdoor air is supplied to second heat exchanger (W2) which is condenser (2), after the monitored parameter obtains the required value and/or after temperature in conditioned space (P) obtains required value, air from the conditioned space is supplied to condenser (2) and back to the conditioned space, and outdoor air is supplied to evaporator (1) and after temperature in conditioned space (P) obtains the required value the direction of circulation is reversed and air from conditioned space (P) is supplied to evaporator (1) and outdoor air is supplied to condenser (2), the air circulation is repeated several times until required moisture and/or temperature are obtained.

4. The method of claim 1, characterised in that in the cycle of dehumidifying air, air from conditioned space (P) is supplied through first duct (Kl) to first heat exchanger (Wl) which is evaporator (1), and outdoor air is supplied through inner duct (KW) to second heat exchanger (W2) which is condenser (2), after the monitored parameter at evaporator (1) obtains required value defrosting cycle is carried out and/or after temperature in conditioned space (P) obtains required value, outdoor air is periodically supplied to condenser (2) whereas after the air temperature decreases to the minimum threshold value, again indoor air is supplied to the condenser, the cycle of dehumidifying air is terminated after air moisture in conditioned space (P) obtains required value.

5. The method of claim 1, characterised in that the parameter monitored at evaporator (1,1 ') is time of evaporator operation.

6. The method of claim 1, characterised in that the parameter monitored at evaporator (1,1 ') is thickness of frost layer on the evaporator surface.

7. The method of claim 1, characterised in that the parameter monitored at evaporator (1,1') is difference of temperature of air in conditioned space (P) and temperature of the frost surface on the evaporator.

8. The method of claim 1, characterised in that the parameter monitored at evaporator (1,1') is difference of temperature of saturation point in conditioned space (P) and temperature of the frost surface on the evaporator.

9. The method of claim 1, characterised in that the parameter monitored at evaporator (1,1 ') is mass of frost.

10. The method of claim 1, characterised in that the parameter monitored at evaporator (1,1') is difference of pressures of refrigerant in front of and behind the evaporator.

11. The method of claim 1, characterised in that the parameter monitored at evaporator

(1,1') is difference of temperatures of air in front of and behind the evaporator.

12. The method of claim 1, characterised in that the parameter monitored at evaporator (1,1') is temperature of air in conditioned space (P).

13. The method of claim 1, characterised in that the parameter monitored at evaporator (1,1') is relative humidity of air in conditioned space (P).

14. The method of claim 1, characterised in that the parameter monitored at evaporator (1,1') is absolute humidity of air in conditioned space (P).

15. System for regulation of air parameters in conditioned spaces, especially in stores of products sensitive to climatic conditions, composed of

(1) compressor cooling system equipped with heat exchangers, control valves and expansion valve, connected to conditioned space;

(2) system for air circulation connected to conditioned space composed of ventilation ducts equipped with dampers and fans;

(3) electronic system for automatic regulation of cooling circulation; characterised in that conditioned space (P) is connected to main ventilation duct (KG) and auxiliary ducts (K1,K2) connected to the main duct. First auxiliary duct is connected via first heat exchanger (Wl), second auxiliary duct is connected to the main duct via second heat exchanger (W2), and between the heat exchangers is split damper (9) connected to system for automatic control and regulation (17). Auxiliary ducts (K1,K2) are connected to conditioned space (P) by inner air dampers (13,10) and to outdoor space by outer air dampers (12,11). Inner air damper (14) is situated between main duct (KG) and conditioned space (P).

16. The system of claim 15, characterised in that first auxiliary duct (Kl) and second auxiliary duct (K2) are connected to third auxiliary duct (K3), which is connected to conditioned space (P) via inner dampers (13,10).

17. The system of claim 15, characterised in that conditioned space (P) is connected to main duct (KG) via inner duct (KW) and fourth inner air damper (15), and main duct is connected to outdoor space via third outer damper (16).

18. The system of claim 15 or 16, characterised in that main duct (KG) is connected via fourth damper (15) to supply air duct (KZ), which is connected to low-temperature waste heat source (S) contained in air, and main duct is connected to outdoor space via third outer air damper (16).

19. The system of claim 15 or 16 or 17 or 18, wherein split damper (9) is a three-position sequential air damper which can be pivoted by 45°, where in first position "A" first auxiliary ventilation duct (Kl) is connected to conditioned space (P), and in second position "B" second auxiliary ventilation duct (K2) is connected to conditioned space (P), and in null position "0" both ventilation ducts (Kl ,K2) are connected to outdoor space.

20. Apparatus for regulation of air parameters in conditioned spaces, especially in stores of products sensitive to climatic conditions, equipped with refrigeration arrangement including compressor, heat exchangers, evaporator and condenser, connected using pipeline, equipped with expansion valve and control valves containing inlet ducts equipped with air dampers and fans and automatic regulation and control system, characterised in that

(1) conditioned space (P) is connected to main ventilation duct (KG) and first and second auxiliary ducts (K1,K2) connected to the main duct;

(2) main duct (KG) connects conditioned space (P) to outdoor space,

(3) first heat exchanger (Wl) of cooling arrangement is situated between main duct (KG) and first auxiliary duct (Kl);

(4) second heat exchanger (W2) of cooling arrangement is situated between main duct (KG) and second auxiliary duct (K2);

(5) split damper (9) is situated between the heat exchangers, connected to system for automatic control and regulation (17)

(6) inner dampers (10,13) are situated on the walls of the ducts on the side of conditioned space

(P);

(7) outer dampers (11,12) are situated on the outer walls of the ducts on the side of conditioned space (P);

(8) outer air fan (7) and inner air fan (8) are situated in main duct (KG).

21. The apparatus of claim 20, characterised in that split damper (9) in main duct (KG) is three-position sequential air guide (9) which can be pivoted by 45°, where in first position "A" first auxiliary ventilation duct (Kl) is connected to conditioned space (P), and in second position "B" second auxiliary ventilation duct (K2) is connected to conditioned space (P), and in null position "0" both ventilation ducts (K1,K2) are connected to outdoor space.

22. The apparatus of claim 20, characterised in that first heat exchanger (Wl) and second heat exchanger (W2) are situated parallelly and opposite to each other.

23. The apparatus of claim 20, characterised in that outer air fan (7) is situated at inlet of main duct (KG) while inner air fan (8) is situated at outlet of the main duct to conditioned space (P).