JP2021025760A - Air-conditioning system and air-conditioning method - Google Patents

Abstract

To provide an air-conditioning system which can prevent the intrusion of high-humidity hot air from outside air accompanied by loading and unloading while maintaining a temperature environment of an F-class cargo handling room.SOLUTION: An air-conditioning system 1 has: a first CO2 circulation path 11 in which a first CO2 refrigerant for cooling an F-class cooling room circulates; a second CO2 circulation path 21 in which a second CO2 refrigerant for cooling a C-class cooling room circulates; a desiccant air conditioner 30 having a desiccant rotor 34 for adsorbing the water vapor of treated air which is obtained by treating outside air; an outside air pre-cooling heat exchanger 31B for cooling and dehumidifying the treated air by a second brine which exchanges heat with the second CO2 refrigerant circulating in the second CO2 circulation path; an air cooling coil 90 for cooling the treated air to which the water vapor is absorbed by the desiccant rotor, by a first brine which exchanges heat with the first CO2 refrigerant circulating in the first CO2 circulation path; and a first blowout part 100 for supplying the treated air which is cooled by the air cooling coil into an F-class cargo handling room R1 corresponding to the F-class cooling room.SELECTED DRAWING: Figure 1

Description

The present invention relates to air conditioning equipment and air conditioning methods used in low temperature freezing and refrigerating warehouses.

A low-temperature freezing and refrigerating warehouse is known in which a low-temperature CO ₂ refrigerant liquid is circulated to be guided to an air cooler in a cooling chamber, and the cooling chamber is cooled by a heat exchanger fan of the air cooler (for example, Patent Document 1). ..

In a class F freezer that keeps the temperature inside the refrigerator below -25 ° C and stores cold storage products, _{the CO 2} refrigerant liquid stored in the _{low-temperature CO 2} receiver is cooled by air in the cooling chamber at, for example, -32 ° C. It is sent to the vessel and exchanges heat with the air in the cooling chamber by the heat exchanger fan to cool the air in the cooling chamber and keep the chamber temperature below the F class level of -25 ° C. _{The CO 2} refrigerant liquid after heat exchange _{returns to the CO 2} receiver, is cooled and liquefied in the primary refrigeration cycle, and is stored in the _{CO 2 receiver.}

On the other hand, in order to store chilled products such as vegetables, milk, and yogurt, a cooling chamber having a cooling chamber temperature of + 10 ° C to -5 ° C, which is a class C level, is also provided in a low-temperature freezing and refrigerating warehouse. _{For example, a CO 2} refrigerant liquid at −7 ° C. is sent to the air cooler in the class C cooling chamber.

In a low-temperature freezing and refrigerating warehouse that uses both an F-class cooling chamber and a C-class cooling chamber, the -32 ° C first CO ₂ refrigerant liquid circulation path used for cooling the F-class cooling chamber and C-class cooling A -7 ° C second CO ₂ refrigerant liquid circulation path used for cooling the chamber is provided.

A general refrigerator has a cargo handling room for carrying out work when taking in and out cold storage products, and is kept at a temperature of 0 to 10 ° C. that does not allow the cold heat of the refrigerator to escape and does not interfere with the work. (For example, Patent Document 2)

JP-A-2015-222145 JP-A-2014-115022

In the low temperature distribution chain, dew condensation and the like generated on the cold storage products during the work of the temporary cargo handling room have been a big problem in low temperature control.

In the F-class low-temperature distribution warehouse, as described in the above-mentioned prior literature, the room temperature of the cargo handling room is kept at a temperature of 0 to 10 ° C. that does not allow the cold heat of the refrigerator to escape and does not interfere with the work. Was there. For this reason, the products stored in the F-class low-temperature storage are in a state where the temperature of the low-temperature distribution chain is interrupted in the cargo handling room, which has been an important problem for maintaining quality. In order to solve this problem, it is required to change the room noise of the cargo handling chamber to a low temperature handling chamber having a low temperature similar to that of the F class temperature. However, in order to make the cargo handling chamber a low temperature handling chamber with a low temperature similar to the F class temperature, the floor surface is -15 ° C to -25 ° C, so the high humidity warm air from the outside air due to loading and unloading. As soon as there is an intrusion, the ice link state will occur, causing problems such as people falling over and slipping of forklifts, and problems such as the cooler that cools the low temperature handling room immediately frosts due to the warm air of the outside air. There is. In addition, the surface of the cold storage product may condense or freeze, which may reduce the commercial value.

The present invention has been invented in order to solve the above problems, and in the F-class cargo handling chamber, while maintaining the temperature environment, it prevents the intrusion of high-humidity warm air from the outside air due to warehousing and delivery, and also An object of the present invention is to provide an air-conditioning system and an air-conditioning method capable of preventing frost formation of an air cooler.

The air-conditioning equipment according to the present invention that achieves the above object is an air-conditioning equipment used in a low-temperature freezing and refrigerating warehouse. Air conditioning equipment, the 2CO ₂ circulation path and the 1 CO ₂ circulation path first 1 CO ₂ refrigerant used to cool the class F of the cooling chamber is circulated, the first 2CO ₂ refrigerant used to cool the C class of the cooling chamber circulates And heat exchange with a desiccant air conditioner including a desiccant rotor that adsorbs water vapor contained in the air to be treated in which the outside air is treated, and a _{second CO 2} refrigerant provided in the desiccant air conditioner and circulating in the second CO 2 circulation path. By the desiccant rotor, the heat exchanger for outside air precooling that cools and dehumidifies the air to be treated and the first brine that exchanges heat with the first _{CO 2} refrigerant that circulates in the _{first CO 2 circulation path.} An air cooling coil that cools the air to be processed to which water vapor is adsorbed and the air to be processed cooled by the air cooling coil are supplied to a class F cargo handling chamber corresponding to the class F cooling chamber. It has one blowout portion and.

Further, the air conditioning method according to the present invention that achieves the above object is an air conditioning method used in a low temperature freezing and refrigerating warehouse. The air conditioning method includes a take-in step of taking in the outside air into the desiccant air conditioner and a second brine that exchanges heat with the second _{CO 2 refrigerant circulating in the second} CO 2 circulation path in the take-in step of taking in the outside air into the desiccant air conditioner. A cooling dehumidification step of cooling and dehumidifying by the method, an adsorption step of adsorbing water vapor contained in the air to be treated in which the outside air is cooled and dehumidified in the cooling and dehumidifying step by a desiccant rotor provided in the desiccant air conditioner, and the adsorption step. The cooling step of cooling the air to be treated that has been adsorbed and dehumidified in the first CO ₂ circulation path by _{a first brine that exchanges heat with the first CO 2} refrigerant circulating in the first CO 2 circulation path, and the cooling step of cooling the air to be treated that has been cooled in the cooling step are F. It has a blow-out process of supplying air to a class F cargo handling room corresponding to a class cooling room.

According to the above-mentioned air-conditioning equipment and air-conditioning method, the air to be processed cooled by the first brine is supplied to the F-class cargo handling chamber. Therefore, the pressure in the F-class cargo handling chamber can be positive while maintaining the low temperature state of the F-class cargo handling chamber. Further, the dew point temperature of the air to be processed can be lowered by the heat exchanger for precooling the outside air and the desiccant air conditioner. Therefore, in the F-class cargo handling chamber, it is possible to prevent the intrusion of high-humidity warm air from the outside air due to the entry and exit, and to prevent the frost formation of the air cooler, while maintaining the temperature environment.

It is the schematic which shows the air-conditioning equipment which concerns on 1st Embodiment of this invention. It is the schematic which shows the air-conditioning equipment which concerns on 2nd Embodiment of this invention. It is the schematic which shows the state that the air to be processed which is supplied from the 1st blowing part is blown down toward a heat insulating door. It is a figure corresponding to FIG. 3 which shows the modification of a heat insulating door. It is a figure which shows the deformation example of a heat insulating door.

<First Embodiment>
Hereinafter, the first embodiment of the present invention will be described with reference to FIG. In the description of the drawings, the same elements are designated by the same reference numerals, and duplicate description will be omitted. The dimensional ratios in the drawings are exaggerated for convenience of explanation and may differ from the actual ratios.

FIG. 1 is a schematic view showing an air conditioner 1 according to a first embodiment of the present invention.

The air conditioning equipment 1 according to the first embodiment is used in a low-temperature freezing and refrigerating warehouse. Specifically, the air conditioning equipment 1 can be suitably used for the cargo handling chambers R1 and R2 facing the outside air on the first floor. Here, the cargo handling chamber R1 is a cargo handling chamber adjacent to the F class cooling chamber, and corresponds to the F class cargo handling chamber. Further, the cargo handling chamber R2 is a cargo handling chamber adjacent to the C-class cooling chamber, and corresponds to a C-class cargo handling chamber. In the following description, the air before being taken into the desiccant air conditioner 30 is referred to as outside air, and the air after being cooled and dehumidified by the heat exchanger 31B for precooling the outside air is referred to as air to be treated.

As shown in FIG. 1, the air conditioning equipment 1 includes a first refrigeration system 10 for a class F cooling chamber, a second refrigeration system 20 for a class C cooling chamber, and a desiccant air conditioner 30 including a desiccant rotor 34. , The first brine circuit 40 that circulates the first brine that exchanges heat with the first _{CO 2 refrigerant that circulates in the first refrigeration system 10, and the first CO 2} refrigerant and the first brine circuit 40 that circulate in the first refrigeration system 10. The first plate heat exchanger 50 that exchanges heat between the first brines, the second brine circuit 60 that circulates the second brine that exchanges heat with the second _{CO 2 refrigerant that circulates in the second refrigeration system 20, and the second refrigeration. A second plate heat exchanger 70 that exchanges heat between the second CO 2} refrigerant that circulates in the system 20 and the second brine that circulates in the second brine circuit 60, and a second refrigeration system 20 that is provided downstream of the desiccant air conditioner 30. A pressure-resistant air cooling coil 80 that cools the air to be processed by the circulating second CO ₂ refrigerant, an air cooling coil 90 that cools the air to be processed by the first brine that circulates in the first brine circuit 40, and a class F cooling chamber. The first blowout unit 100 that supplies air to be processed to the F-class cargo handling chamber R1 corresponding to the above, and the first air to be supplied to the C-class cargo handling chamber R2 corresponding to the C-class cooling chamber. The first air cooler 120 that cools the air in the F-class cargo handling chamber R1 by the _{second blowout unit 110 and the first CO 2} refrigerant that circulates in the first refrigeration system 10, and the second CO that circulates in the second refrigeration system 20. _It has a second air cooler 130 that cools the air in the class C cargo handling chamber R2 with two refrigerants.

The first refrigeration system 10, as shown in FIG. 1, and the 1 CO ₂ circulation path 11 first 1 CO ₂ refrigerant used to cool the class F of the cooling chamber is circulated, for storing the first 1 CO ₂ refrigerant first 1 CO _{It has two} receivers 12 and a first ammonia refrigeration cycle 13 in which an ammonia refrigerant circulates.

As shown in FIG. 1, the first _{CO 2} circulation path 11 is configured to circulate the _{first CO 2 refrigerant.} The first CO ₂ circulation path 11 is a first CO ₂ feed line 11A that sends the _{first CO 2 refrigerant from the first CO 2} receiver 12 to the first plate heat exchanger 50, and a first plate heat exchanger 50. It has a _{first CO 2} return line 11B for returning the _{1CO 2} refrigerant to the first CO ₂ receiver 12, and a first reliquefaction line 11C for reliquefying the gasified first _{CO 2 refrigerant.}

The first CO ₂ feed line 11A is connected below the _{first CO 2 receiver 12.} Further, the first CO ₂ return line 11B is connected above the _{first CO 2 receiver 12.}

A first pump P1 is provided in the first _{CO 2} feed line 11A, and the liquid first CO _{2 refrigerant in the first CO 2} receiver 12 flows to the first plate heat exchanger 50 by the first pump P1.

Further, the first CO ₂ circulation path 11 _{is connected to a third CO 2} circulation path 15 that _{branches from the first CO 2} feed line 11A, passes through the first air cooler 120, and _{returns to the first CO 2} return line 11B. ing.

Temperature of the 1 CO ₂ refrigerant circulating in the first 1 CO ₂ circulation path 11 and the 3CO ₂ circulation path 15 is, for example, -32 ° C..

The first reliquefaction line 11C is connected above the _{first CO 2 receiver 12.} The gaseous first CO _{2 refrigerant in the first CO 2} receiver 12 is reliquefied by the first ammonia refrigeration cycle 13 as it passes through the first reliquefaction line 11C. Then, the reliquefied liquid first CO ₂ refrigerant returns to the first CO _{2 receiver 12.}

Ammonia refrigerant circulates in the first ammonia refrigeration cycle 13. The first ammonia refrigeration cycle 13 cools and liquefies the _{gaseous first CO 2 refrigerant.} The first ammonia refrigeration cycle 13 includes a first 1 CO ₂ liquefier 14, and the refrigerator, a condenser, an ammonia receiver, an expansion valve, an. Since a known ammonia two-stage compression refrigeration cycle can be used as the first ammonia refrigeration cycle 13, detailed description thereof will be omitted here.

The second refrigeration system 20, as shown in FIG. 1, first and second 2CO ₂ circulation path 21 first 2CO ₂ refrigerant circulates used to cool the C class of the cooling chamber, for storing the first 2CO ₂ refrigerant 2CO _{It has two} receivers 22 and a second ammonia refrigeration cycle 23 in which an ammonia refrigerant circulates.

As shown in FIG. 1, the _second CO 2 circulation path 21 is configured to circulate the _{second CO 2 refrigerant.} The _second CO 2 circulation path 21 is a _{second CO 2} feed line 21A that sends a _second CO 2 refrigerant from the second CO 2 receiver 22 to the second plate heat exchanger 70, and a second plate heat exchanger 70. It has a _{second CO 2} return line 21B for returning the 2CO 2 refrigerant to the second CO ₂ receiver 22, and a second reliquefaction line 21C for reliquefying the gasified _{second CO 2 refrigerant.}

The _second CO 2 feed line 21A is connected below the _{second CO 2 receiver 22.} Further, the second CO ₂ return line 21B is connected above the _{second CO 2 receiver 22.}

A second pump P2 is provided in the second CO ₂ feed line 21A, and the liquid second CO _{2 refrigerant in the second CO 2} receiver 22 flows to the second plate heat exchanger 70 by the second pump P2.

Further, in the first 2CO ₂ circulation path 21 branches from the 2CO ₂ feed line 21A, through the breakdown voltage type air cooling coil 80, the 4CO ₂ circulation path 25 is connected back to the 2CO ₂ return line 21B ing.

Further, in the first 4CO ₂ circulation path 25 branches from the 4CO ₂ circulation path 25, passes through the second air cooler 130, the 5Co ₂ circulation path 26 back to the 4CO ₂ circulation path 25 is connected ing.

The second reliquefaction line 21C is _{connected above the second} CO2 receiver 22. The _{gaseous second CO 2 refrigerant in the second CO 2} receiver 22 is reliquefied by the second ammonia refrigeration cycle 23 as it passes through the second reliquefaction line 21C. Then, the reliquefied liquid second CO ₂ refrigerant returns to the _{second CO 2 receiver 22.}

In the second ammonia refrigeration cycle 23, the ammonia refrigerant circulates. The second ammonia refrigeration cycle 23 cools and liquefies the gaseous _{second CO 2 refrigerant.} Second ammonia refrigeration cycle 23 includes a first 2CO ₂ liquefier 24, and refrigerator, a condenser, an ammonia receiver, an expansion valve, an. Since a known ammonia single-stage compression refrigeration cycle can be used as the second ammonia refrigeration cycle 23, detailed description thereof will be omitted here.

In the desiccant air conditioner 30, as shown in FIG. 1, the adjusting chamber 31 and the regeneration chamber 32 are arranged side by side with the partition wall 33 interposed therebetween. The adjusting chamber 31 is provided with a first suction fan 31A, an outside air precooling heat exchanger 31B, and a dew point temperature sensor 31C. The reproduction chamber 32 is provided with a second suction fan 32A and a regeneration heater 32B. Further, in the desiccant air conditioner 30, a desiccant rotor 34 is arranged across the adjustment chamber 31 and the regeneration chamber 32.

The first suction fan 31A and the second suction fan 32A form an air flow in opposite directions in the adjusting chamber 31 and the regeneration chamber 32.

The outside air cooled and dehumidified by the outside air precooling heat exchanger 31B is taken into the adjusting chamber 31 by the first suction fan 31A.

The outside air precooling heat exchanger 31B exchanges _{heat with the second CO 2} refrigerant circulating in the _{second CO 2} circulation path 21, and cools and dehumidifies the outside air by the second brine circulating in the second brine circuit 60. The dew point temperature sensor 31C measures the dew point temperature of the air to be treated that has been cooled and dehumidified.

The outside air precooling heat exchanger 31B is generally large in size because it exchanges heat between the second brine circulating in the second brine circuit 60 and the outside air. However, since the second brine circulating in the second brine circuit 60 is not high pressure, an inexpensive general desiccant air conditioner 30 precooling coil (plate fin tube heat exchanger) can be used.

The desiccant rotor 34 is rotatably arranged around a rotation axis (not shown). The desiccant rotor 34 carries an adsorbent, and in the adjusting chamber 31, the desiccant rotor 34 adsorbs and removes water vapor contained in the air to be treated. The region where the water vapor of the desiccant rotor 34 is adsorbed moves to the regeneration chamber 32, and in the regeneration chamber 32, the adsorbed water vapor is released to the regeneration air by the heat possessed by the regeneration air. The desiccant rotor 34 is formed on a honeycomb with a special sheet impregnated with an adsorbent. As the adsorbent, for example, an inorganic adsorbent such as silica gel or zeolite, or a polymer adsorbent is used.

When the adsorbent adsorbs water vapor, it releases heat of adsorption, so that the temperature of the air to be treated after passing through the desiccant rotor 34 rises from that before passing.

Outside air is taken into the reproduction chamber 32 by the second suction fan 32A. The outside air taken into the regeneration chamber 32 is heated by the regeneration heater 32B. The air heated by the regeneration heater 32B is sent to the desiccant rotor 34 as regeneration air, and the water vapor adsorbed on the desiccant rotor 34 is released by the retained heat heated by the regeneration heater 32B.

As shown in FIG. 1, the first brine circuit 40 is arranged so as to connect the first plate heat exchanger 50 and the air cooling coil 90. The first brine circulates in the first brine circuit 40. The first brine in the first brine circuit 40 is circulated by the third pump P3. The first brine circulating in the first brine circuit 40 is cooled in the first plate heat exchanger 50, for example, from -20 ° C to -25 ° C, and heated in the air cooling coil 90, for example, from -25 ° C to -20 ° C. Will be done.

As shown in FIG. 1, the first plate heat exchanger 50 _{heats between the first CO 2 refrigerant circulating in the first CO 2} circulation path 11 of the first refrigeration system 10 and the first brine circulating in the first brine circuit 40. Exchange. Since a known plate heat exchanger can be used as the first plate heat exchanger 50, detailed description thereof will be omitted here.

As shown in FIG. 1, the second brine circuit 60 is arranged so as to connect the second plate heat exchanger 70 and the outside air precooling heat exchanger 31B. The second brine circulates in the second brine circuit 60. The second brine in the second brine circuit 60 is circulated by the fourth pump P4. The second brine circulating in the second brine circuit 60 is cooled in the second plate heat exchanger 70, for example, from 5 ° C. to 0 ° C., and heated in the outside air precooling heat exchanger 31B, for example, from 0 ° C. to 5 ° C. To.

As shown in FIG. 1, the second plate heat exchanger 70 _{heats between the second CO 2 refrigerant circulating in the second CO 2} circulation path 21 of the second refrigerating system 20 and the second brine circulating in the second brine circuit 60. Exchange. Since a known plate heat exchanger can be used as the second plate heat exchanger 70, detailed description thereof will be omitted here.

The pressure-resistant air cooling coil 80 is provided downstream of the desiccant air conditioner 30. A first flow passage 81 through which the air to be processed by the desiccant air conditioner 30 flows is provided between the desiccant air conditioner 30 and the pressure resistant air cooling coil 80. A first damper D1 is provided in the first flow passage 81. The opening and closing of the first damper D1 is performed by a control unit (not shown).

Further, downstream of the desiccant air conditioner 30, a branch path 84 that branches from the first flow passage 81 and can exhaust the air to be treated by the desiccant air conditioner 30 to the outside is provided. A second damper D2 is provided on the branch road 84. The opening and closing of the second damper D2 is performed by a control unit (not shown).

In the pressure-resistant air cooling coil 80, the air to be processed that has flowed through the first flow passage 81 is cooled to, for example, from 28 ° C. to 3 ° C. by the _second CO 2 refrigerant circulating in the _{fourth CO 2 circulation path 25.}

A second flow passage 82 through which the air to be processed, which has been cooled by the pressure-resistant air cooling coil 80, flows is provided between the pressure-resistant air cooling coil 80 and the second blowing portion 110.

Between the pressure-resistant air cooling coil 80 and the air cooling coil 90, a third flow passage 83 through which the air to be processed cooled by the pressure-resistant air cooling coil 80 flows is provided. The third flow passage 83 is configured to branch from the second flow passage 82.

In the air cooling coil 90, the air to be processed that has flowed through the third flow passage 83 is cooled to, for example, from 3 ° C. to -13 ° C. by the first brine circulating in the first brine circuit 40.

A fourth flow passage 91 through which the air to be processed cooled by the air cooling coil 90 flows is provided between the air cooling coil 90 and the first blowing portion 100.

As the air cooling coil 90, an inexpensive general air coil (plate fin tube heat exchanger) can be used because the first brine circulating in the first brine circuit 40 is not high pressure.

As shown in FIG. 1, the first blowing unit 100 supplies the F-class cargo handling chamber R1 with the air to be processed cooled by the air cooling coil 90. Specifically, as shown in FIG. 3, the air to be supplied from the first blowout unit 100 is blown down toward the center of the heat insulating door G1 provided in the F-class cargo handling chamber R1. The first blowing unit 100 is provided in the F-class cargo handling chamber R1. The number of first blowout portions 100 provided is not particularly limited, but is, for example, five. In this way, in order to supply the air to be processed cooled by the air cooling coil 90 to the F-class cargo handling chamber R1, the first blowing unit 100 creates a positive pressure inside the F-class cargo handling chamber R1. It is possible to preferably prevent high humidity warm air from entering from the outside. In addition, the temperature environment of the F-class cargo handling chamber R1 can be maintained. At this time, the pressure of the F-class cargo handling chamber R1 is, for example, atmospheric pressure + 32 Pa. Further, the air to be processed supplied from the first blowout unit 100 is blown down toward the center of the heat insulating door G1 of the F-class cargo handling chamber R1, so that when the heat insulating door G1 is opened, moisture from the outside is generated. It is irradiated with warm air (moving upward in the vertical direction). Therefore, since the warm water dissolves in the dry air to be treated that has been blown down, the occurrence of dew condensation and frost formation can be suitably prevented. The configuration of the heat insulating door G1 is not limited to the pull-out type configuration shown in FIG. 3, and is a known heat insulating door (for example, the sliding heat insulating door G3 shown in FIG. 4) or a known heat insulating door (for example, FIG. 5). It may be the oversliding type heat insulating door G4) shown.

As shown in FIG. 1, the second blowout unit 110 supplies the C-class cargo handling chamber R2 with the air to be processed cooled by the pressure-resistant air cooling coil 80. Specifically, similarly to the first blowing unit 100 shown in FIG. 3, the air to be processed supplied from the second blowing unit 110 is directed toward the center of the heat insulating door G2 provided in the C-class cargo handling chamber R2. Is blown down (see Fig. 1). The second blowout unit 110 is provided in the C-class cargo handling chamber R2. The number of the second blowing portions 110 provided is not particularly limited, but is, for example, five. In this way, the second blowout unit 110 positively pressurizes the inside of the C-class cargo handling chamber R2 in order to supply the C-class cargo handling chamber R2 with the air to be processed cooled by the pressure-resistant air cooling coil 80. It is possible to preferably prevent high humidity warm air from entering from the outside. In addition, the temperature environment of the C-class cargo handling chamber R2 can be maintained. The pressure of the C-class cargo handling chamber R2 at this time is, for example, atmospheric pressure + 32 Pa. Further, the air to be processed supplied from the second blowout unit 110 is blown down toward the center of the heat insulating door G2 of the C-class cargo handling chamber R2, so that when the heat insulating door G2 is opened, moisture from the outside is generated. It is irradiated with warm air (moving upward in the vertical direction). Therefore, since the warm water dissolves in the dry air to be treated that has been blown down, the occurrence of dew condensation and frost formation can be suitably prevented.

As shown in FIG. 1, the first air cooler 120 is provided in the F-class cargo handling chamber R1. By first fan F1 is rotated in the first air cooler 120, by a 1 CO ₂ refrigerant circulating in the first 3CO ₂ circulation path 15, F-class the handling chamber R1 is cooled. Here, since the dew point temperature of the air to be treated is −30 ° C., the generation of frost can be prevented in the first air cooler 120.

As shown in FIG. 1, the second air cooler 130 is provided in the class C cargo handling chamber R2. As the second fan F2 rotates in the second air cooler 130, the C-class cargo handling chamber R2 is cooled _{by the second CO 2} refrigerant circulating in the _{fifth CO 2 circulation path 26.}

Next, an air conditioning method using the air conditioning equipment 1 according to the first embodiment will be described with reference to FIG.

First, the outside air is taken into the desiccant air conditioner 30 (take-in process). At this time, the outside air is sucked into the desiccant air conditioner 30 by the first suction fan 31A in the adjusting chamber 31. The outside air before being taken into the desiccant air conditioner 30 is, for example, a temperature of 35 ° C., a humidity of 60%, and a dew point temperature of 26 ° C.

Then, the outside air taken into the desiccant air conditioner 30 is cooled and dehumidified by the outside air precooling heat exchanger 31B (cooling dehumidification step). The temperature of the air to be treated, which has been cooled and dehumidified by the heat exchanger 31B for precooling the outside air, is, for example, 5 ° C. Specifically, the air taken into the desiccant air conditioner 30 is cooled and dehumidified by the second brine that exchanges heat with the second _{CO 2} refrigerant circulating in the _{second CO 2 circulation path 21.} The second brine circulating in the second brine circuit 60 raises the temperature from 0 ° C. to 5 ° C. by cooling and dehumidifying the outside air taken into the desiccant air conditioner 30.

Then, the air to be treated is adsorbed and dehumidified by the desiccant rotor 34 to adsorb the water vapor contained in the air to be treated (adsorption step). In the adsorption step, the air to be treated on which water vapor is adsorbed is exhausted by closing the first damper D1 and opening the second damper D2 until the dew point stabilizes. Then, when the dew point of the air to be treated on which water vapor is adsorbed becomes stable, the first damper D1 is opened and the second damper D2 is closed, so that the pressure-resistant air cooling coil is passed through the first flow passage 81. It will be distributed toward 80. The air to be treated at this time is, for example, a temperature of 28 ° C., a humidity of 1%, and a dew point temperature of −30 ° C.

As described above, the outside air sucked by the first suction fan 31A is cooled and dehumidified by the outside air precooling heat exchanger 31B, and then adsorbed and dehumidified by the desiccant rotor 34. Therefore, the dehumidifying load of the desiccant rotor 34 is reduced and the life can be extended as compared with the case where the desiccant rotor 34 is adsorbed and dehumidified without being cooled and dehumidified by the outside air precooling heat exchanger 31B.

Then, the air to be processed that has flowed through the first flow passage 81 is cooled in the pressure resistant air cooling coil 80 by the second CO _{2 refrigerant circulating in the fourth CO 2} circulation path 25, for example, from 28 ° C. to 3 ° C.

Then, in the pressure-resistant air cooling coil 80, the air to be processed, which has been cooled from 28 ° C. to 3 ° C., flows to the second blowout portion 110 via the second flow passage 82, and is class C by the second blowout portion 110. Air is supplied to the inside of the cargo handling chamber R2. At this time, the temperature in the class C cargo handling chamber R2 is, for example, 0 ° C to + 5 ° C.

On the other hand, in the pressure-resistant air cooling coil 80, the air to be processed cooled from 28 ° C. to 3 ° C. flows to the air cooling coil 90 via the third flow passage 83.

Then, the air to be processed that has flowed through the third flow passage 83 is cooled in the air cooling coil 90 by the first brine circulating in the first brine circuit 40, for example, from 3 ° C. to -13 ° C. (cooling step). ..

Then, in the air cooling coil 90, the air to be processed, which has been cooled from 3 ° C. to -13 ° C., flows to the first blowout portion 100 via the fourth flow passage 91, and is of class F by the first blowout portion 100. Air is supplied to the inside of the cargo handling chamber R1 (air supply process). At this time, the temperature in the F-class cargo handling chamber R1 was −15 ° C.

As described above, the air-conditioning equipment 1 according to the present embodiment is the air-conditioning equipment 1 used in the low-temperature freezing and refrigerating warehouse. Air conditioning 1, first 2CO and the 1 CO ₂ circulation path 11 first 1 CO ₂ refrigerant used to cool the class F of the cooling chamber is circulated, the first 2CO ₂ refrigerant used to cool the C class of the cooling chamber to circulate ₂ A desiccant air conditioner 30 including a circulation path 21 and a desiccant rotor 34 for adsorbing water vapor contained in the air to be treated with the outside air, and a second CO provided in the desiccant air conditioner 30 and _{circulating in the second CO 2} circulation path 21. ₂ The desiccant is made by the heat exchanger 31B for outside air precooling that cools and dehumidifies the air to be treated by the second brine that exchanges heat with the refrigerant, and the first brine that exchanges heat with the first _{CO 2} refrigerant that circulates in the _{first CO 2 circulation path 11.} The air cooling coil 90 that cools the air to be processed to which the water vapor is adsorbed by the rotor 34 and the air to be processed cooled by the air cooling coil 90 are inside the class F cargo handling chamber R1 corresponding to the class F cooling chamber. It has a first blowout unit 100 for supplying air to the air. According to the air-conditioning equipment 1 configured in this way, the air to be processed cooled by the first brine is supplied into the F-class cargo handling chamber R1. Therefore, the pressure inside the F-class cargo handling chamber R1 can be positive while maintaining the low temperature state of the F-class cargo handling chamber R1. Further, the dew point temperature of the air to be treated can be lowered to −30 ° C. by the heat exchanger 31B for precooling the outside air and the desiccant air conditioner 30. Therefore, in the F-class cargo handling chamber R1, while maintaining the temperature environment, it is possible to prevent the intrusion of high-humidity warm air from the outside air due to the entry and exit, and to prevent the frost formation of the first air cooler 120. ..

Further, the air conditioning equipment 1 is provided between the desiccant air conditioner 30 and the air cooling coil 90 in the flow passage of the air to be treated, and the air to be treated in which water vapor is adsorbed by the desiccant rotor 34 is cooled by the _{second CO 2 refrigerant.} A pressure-resistant air cooling coil 80, a second blowout unit 110 that supplies air cooled by the pressure-resistant air cooling coil 80 into a class C cargo handling chamber R2 corresponding to a class C cooling chamber, and Further have. According to the air-conditioning equipment 1 configured in this way, the inside of the C-class cargo handling chamber R2 can be positively pressured while maintaining the low temperature state of the C-class cargo handling chamber R2.

Further, the air conditioning equipment 1 is provided with a first damper D1 provided in the first flow passage 81 of the air to be processed and a branch path 84 branched from the first flow passage 81 of the air to be processed and communicate with the exhaust port. It has a second damper D2 provided in the. According to the air-conditioning equipment 1 configured in this way, the air to be processed can be exhausted by closing the first damper D1 and opening the second damper D2 until the dew point stabilizes.

Further, as described above, the air conditioning method according to the present embodiment is an air conditioning method used in a low-temperature freezing and refrigerating warehouse. The air conditioning method includes a take-in step of taking in the outside air into the desiccant air conditioner 30, and a second brine that exchanges heat of the _{outside air taken into the desiccant air conditioner 30 with the second CO 2 refrigerant circulating in the second CO 2} circulation path 21 in the take-in step. In the cooling dehumidification step of cooling and dehumidifying, and the adsorption step of adsorbing the water vapor contained in the air to be treated in which the outside air is cooled and dehumidified in the cooling and dehumidifying step by the desiccant rotor 34 provided in the desiccant air conditioner 30, and the adsorption step. A cooling step in which the dehumidified air to be treated _{is cooled by a first brine that exchanges heat with the first CO 2 refrigerant circulating in the first CO 2} circulation path 11, and a cooling step in which the air to be treated cooled in the cooling step is cooled in a class F cooling chamber. It has an air supply process for supplying air to the F-class cargo handling chamber R1 corresponding to the above. According to this air conditioning method, the air to be processed cooled by the first brine is supplied into the F-class cargo handling chamber R1. Therefore, the pressure inside the F-class cargo handling chamber R1 can be positive while maintaining the low temperature state of the F-class cargo handling chamber R1. Further, the dew point temperature of the air to be treated can be lowered to −30 ° C. by the heat exchanger 31B for precooling the outside air and the desiccant air conditioner 30. Therefore, in the F-class cargo handling chamber R1, while maintaining the temperature environment, it is possible to prevent the intrusion of high-humidity warm air from the outside air due to the entry and exit, and to prevent the frost formation of the first air cooler 120. ..

<Second Embodiment>
Next, the configuration of the air conditioning equipment 2 according to the second embodiment of the present invention will be described with reference to FIG. FIG. 2 is a schematic view showing the air conditioning equipment 2 according to the second embodiment of the present invention.

The parts common to the first embodiment will be omitted, and the parts characterized only in the second embodiment will be described. The same members as those in the first embodiment described above will be described with the same reference numerals, and duplicate description will be omitted. The second embodiment is different from the first embodiment in that the C-class cargo handling chamber R2 is not provided.

As shown in FIG. 2, the air conditioning equipment 2 includes a first refrigeration system 10 for a class F cooling chamber, a second refrigeration system 20 for a class C cooling chamber, and a desiccant air conditioner 30 including a desiccant rotor 34. , The first brine circuit 40 that circulates the first brine that exchanges heat with the first _{CO 2 refrigerant that circulates in the first refrigeration system 10, and the first CO 2} refrigerant and the first brine circuit 40 that circulate in the first refrigeration system 10. The first plate heat exchanger 50 that exchanges heat between the first brines, the second brine circuit 60 that circulates the second brine that exchanges heat with the second _{CO 2 refrigerant that circulates in the second refrigeration system 20, and the second refrigeration. The air to be treated by the second plate heat exchanger 70 that exchanges heat between the second CO 2} refrigerant circulating in the system 20 and the second brine circulating in the second brine circuit 60, and the first brine circulating in the first brine circuit 40. The air cooling coil 190 that cools the air, the first blowout unit 100 that supplies the air to be processed to the F class cargo handling chamber R1 corresponding to the F class cooling chamber, and the first CO _{2 that circulates in the first refrigeration system 10.} It has a first air cooler 120 that cools the air in the F-class cargo handling chamber R1 with a refrigerant.

1st refrigeration system 10, 2nd refrigeration system 20, desiccant air conditioner 30, 1st brine circuit 40, 1st plate heat exchanger 50, 2nd brine circuit 60, 2nd plate heat exchanger 70, 1st blowout unit 100 , And the configuration of the first air cooler 120 is the same configuration as the air conditioning equipment 1 according to the first embodiment described above, and thus the description thereof will be omitted.

As shown in FIG. 2, the air cooling coil 190 is provided downstream of the desiccant air conditioner 30. A fifth flow passage 191 through which the air to be processed by the desiccant air conditioner 30 flows is provided between the desiccant air conditioner 30 and the air cooling coil 190. A first damper D1 is provided in the fifth flow passage 191. The opening and closing of the first damper D1 is performed by a control unit (not shown).

Further, downstream of the desiccant air conditioner 30, a branch path 192 that branches from the fifth flow passage 191 and can exhaust the processed air treated by the desiccant air conditioner 30 to the outside is provided. A second damper D2 is provided on the branch road 192. The opening and closing of the second damper D2 is performed by a control unit (not shown).

In the air cooling coil 190, the air to be processed that has flowed through the fifth flow passage 191 is cooled to, for example, from 28 ° C. to -13 ° C. by the first brine circulating in the first brine circuit 40.

A sixth flow passage 193 through which the air to be processed cooled by the air cooling coil 190 flows is provided between the air cooling coil 190 and the first blowing portion 100.

Next, a method of using the air conditioning equipment 2 according to the second embodiment will be described.

First, the outside air is taken into the desiccant air conditioner 30 (take-in process). At this time, the outside air is sucked into the desiccant air conditioner 30 by the first suction fan 31A in the adjusting chamber 31. The outside air before being taken into the desiccant air conditioner 30 is, for example, a temperature of 35 ° C., a humidity of 60%, and a dew point temperature of 26 ° C.

Then, the outside air taken into the desiccant air conditioner 30 is cooled and dehumidified by the outside air precooling heat exchanger 31B (cooling dehumidification step). The temperature of the air to be treated, which has been cooled and dehumidified by the heat exchanger 31B for precooling the outside air, is 5 ° C.

Then, the air to be treated is adsorbed and dehumidified by the desiccant rotor 34 to adsorb the water vapor contained in the air to be treated (adsorption step). In the adsorption step, the air to be treated on which water vapor is adsorbed is exhausted by closing the first damper D1 and opening the second damper D2 until the dew point stabilizes. Then, when the dew point of the air to be treated on which water vapor is adsorbed becomes stable, the first damper D1 is opened and the second damper D2 is closed, so that the air is cooled to the air cooling coil 190 via the fifth flow passage 191. Distribute to. The air to be treated at this time is, for example, a temperature of 28 ° C., a humidity of 1%, and a dew point temperature of −30 ° C.

Then, the air to be processed that has flowed through the fifth flow passage 191 is cooled in the air cooling coil 190 by the first brine circulating in the first brine circuit 40, for example, from 28 ° C. to -13 ° C.

Then, in the air cooling coil 190, the air to be processed, which has been cooled from 28 ° C. to -13 ° C., flows to the first blowout portion 100 via the sixth flow passage 193, and is of class F by the first blowout portion 100. Air is supplied to the inside of the cargo handling chamber R1.

The present invention is not limited to the above-described embodiment, and various modifications can be made within the scope of the claims.

For example, in the first embodiment described above, the air to be processed supplied from the first blowout unit 100 is blown down toward the center of the heat insulating door G1 provided in the F-class cargo handling chamber R1 and blown down to the center of the second blowout. The air to be processed supplied from the unit 110 was blown down toward the center of the heat insulating door G2 provided in the class C cargo handling chamber R2. However, the air to be processed that is supplied from the first blowout unit 100 may be supplied to the F-class cargo handling chamber R1, and the air to be processed that is supplied from the second blowout unit 110 is class C. It suffices to supply air to the cargo handling room R2.

1, 2 air conditioning equipment,
10 1st refrigeration system,
11 1st CO ₂ circulation path,
20 Second refrigeration system,
21 2nd CO ₂ circulation path,
30 desiccant air conditioner,
31B heat exchanger for outside air precooling,
34 desiccant rotor,
40 1st brine circuit,
50 1st plate heat exchanger,
60 Second brine circuit,
70 2nd plate heat exchanger,
80 pressure resistant air cooling coil,
81 First-class passage,
84, 192 fork,
90, 190 air cooling coil,
100 1st blowout part,
110 2nd blowout part,
120 1st air cooler,
130 Second air cooler,
D1 1st damper,
D2 2nd damper,
G1 insulated door,
G2 insulated door,
G3 insulated door,
G4 insulated door,
R1 F class cargo handling room,
R2 C class cargo handling room.

Claims (5)

Air conditioning equipment used in low-temperature freezing and refrigerating warehouses
_{The 1st CO 2} circulation path through which the _{1st CO 2} refrigerant used for cooling the F-class cooling chamber circulates,
A second CO ₂ circulation path through which the _{second CO 2} refrigerant used for cooling the C-class cooling chamber circulates,
A desiccant air conditioner equipped with a desiccant rotor that adsorbs water vapor contained in the air to be treated with the outside air.
An outside air precooling heat exchanger provided in the desiccant air conditioner to cool and dehumidify the air to be processed by a second brine that exchanges heat with the second _{CO 2} refrigerant circulating in the _{second CO 2 circulation path.}
An air cooling coil that cools the air to be processed in which the water vapor is adsorbed by the desiccant rotor by the first brine that exchanges heat with the first _{CO 2} refrigerant that circulates in the first CO _{2 circulation path.}
An air conditioner having a first blowout unit that supplies air cooled by the air cooling coil to an F-class cargo handling chamber corresponding to the F-class cooling chamber. A pressure-resistant type that is provided between the desiccant air conditioner and the air cooling coil in the flow passage of the air to be treated and cools the air to be treated in which the water vapor is adsorbed by the desiccant rotor with the second CO _{2 refrigerant.} With an air cooling coil
The first aspect of the present invention, further comprising a second blowing portion for supplying the air to be processed cooled by the pressure-resistant air cooling coil into the C-class cargo handling chamber corresponding to the C-class cooling chamber. Air conditioning equipment. The air to be processed, which is supplied from the first blowout portion, is blown down toward the center of the heat insulating door provided in the F-class cargo handling chamber.
The air conditioning equipment according to claim 2, wherein the air to be processed supplied from the second blowing portion is blown down toward the center of a heat insulating door provided in the class C cargo handling chamber. The first damper provided in the air flow path to be processed and
The air-conditioning equipment according to any one of claims 1 to 3, further comprising a second damper provided in a branch path that is branched from the flow passage of the air to be processed and communicates with an exhaust port. An air conditioning method used in low-temperature freezing and refrigerating warehouses.
The process of taking in the outside air into the desiccant air conditioner and
In the intake step, a cooling dehumidification step of cooling and dehumidifying the outside air taken into the desiccant air conditioner by a second brine that exchanges heat with the second _{CO 2} refrigerant circulating in the _{second CO 2 circulation path.}
In the cooling / dehumidifying step, the adsorption step of adsorbing the water vapor contained in the air to be treated by which the outside air has been cooled / dehumidified by the desiccant rotor provided in the desiccant air conditioner.
A cooling step of cooling the air to be treated, which has been adsorbed and dehumidified in the adsorption step, by a first brine that exchanges heat with the first _{CO 2} refrigerant circulating in the _{first CO 2 circulation path.}
An air conditioning method including an air supply step of supplying the air to be processed cooled in the cooling step to a class F cargo handling chamber corresponding to a class F cooling chamber.