CN117479998A - Dehumidifying device - Google Patents

Abstract

The dehumidification device (1) is provided with a housing (20), a blower (6), and a refrigerant circuit (10). The refrigerant circuit (10) has a compressor (2), a condenser (3), a pressure reducing device (4), and an evaporator (5), and is configured so that the refrigerant circulates in the order of the compressor (2), the condenser (3), the pressure reducing device (4), and the evaporator (5). The condenser (3) includes a1 st condensation unit (3 a) and a2 nd condensation unit (3 b), and is configured such that the refrigerant flows in the order of the 2 nd condensation unit (3 b) and the 1 st condensation unit (3 a). The 1 st condensation unit (3 b) is disposed downstream of the evaporator (5). The 2 nd condensing unit (3 b) is disposed downstream of the 1 st condensing unit (3 a). The height of the 1 st condensation part (3 a) is lower than the height of the evaporator (5). The height of the 2 nd condensing part (3 b) is lower than the height of the 1 st condensing part (3 a).

Description

Dehumidifying device

Technical Field

The present disclosure relates to a dehumidifying apparatus.

Background

Conventionally, there has been proposed a dehumidifying apparatus in which a condenser is divided into two parts to improve the condensing ability in order to improve the performance of the condenser. For example, international publication No. 2018/154839 (patent document 1) describes a dehumidifier using two condensers. In this dehumidifying apparatus, the height of the condenser on the windward side is the same as the height of the evaporator.

Prior art literature

Patent literature

Patent document 1: international publication No. 2018/154839

Disclosure of Invention

Problems to be solved by the invention

In the dehumidifying apparatus described in the above publication, since the height of the condenser on the windward side is the same as the height of the evaporator, it is impossible to make the air having passed through the evaporator at a low temperature flow into the condenser on the leeward side without passing through the condenser on the windward side. Therefore, the temperature difference between the superheated gas refrigerant flowing from the compressor into the downwind side condenser and the air flowing into the downwind side condenser cannot be increased. Therefore, the heat exchange amount of the condenser cannot be increased.

The present disclosure has been made in view of the above problems, and an object thereof is to provide a dehumidifier that can increase the heat exchange amount of a condenser.

Means for solving the problems

The dehumidifying device of the present disclosure includes a housing, a blower, and a refrigerant circuit. The blower and the refrigerant circuit are disposed within the housing. The blower is configured to send out air. The refrigerant circuit includes a compressor, a condenser, a pressure reducing device, and an evaporator, and is configured to circulate a refrigerant in the order of the compressor, the condenser, the pressure reducing device, and the evaporator. The condenser includes a1 st condensation portion and a2 nd condensation portion, and is configured to flow the refrigerant in the order of the 2 nd condensation portion and the 1 st condensation portion. The 1 st condensation unit is disposed downstream of the evaporator. The 2 nd condensation unit is disposed downstream of the 1 st condensation unit. The height of the 1 st condensation part is lower than the height of the evaporator. The height of the 2 nd condensing part is higher than that of the 1 st condensing part.

Effects of the invention

According to the present disclosure, the 1 st condensation part has a height lower than that of the evaporator, and the 2 nd condensation part has a height higher than that of the 1 st condensation part. Therefore, by bringing the air having passed through the evaporator at a relatively low temperature into contact with the 2 nd condensing portion through which the refrigerant in the superheated gas state passes, the temperature difference between the refrigerant and the air can be increased. This can increase the heat exchange amount of the condenser.

Drawings

Fig. 1 is a refrigerant circuit diagram of the dehumidifying apparatus of embodiment 1.

Fig. 2 is a schematic diagram showing the structure of the dehumidifier of embodiment 1.

Fig. 3 is a cross-sectional view of the evaporator, the 1 st condensation unit, and the 2 nd condensation unit of the dehumidifier of embodiment 1.

Fig. 4 is a cross-sectional view of an evaporator and a condenser of the dehumidifying apparatus of the comparative example of embodiment 1.

Fig. 5 is a diagram showing a relationship between the amount of dehumidification and the amount of refrigerant in the dehumidification device according to embodiment 1.

Fig. 6 is a schematic diagram showing the structure of the dehumidifying device according to embodiment 2.

Fig. 7 is a refrigerant circuit diagram of the dehumidifying apparatus of embodiment 3.

Fig. 8 is a schematic diagram showing the structure of the dehumidifier of embodiment 3.

Fig. 9 is a cross-sectional view of the evaporator, the 1 st condensation unit, the 2 nd condensation unit, and the 3 rd condensation unit of the dehumidifier of embodiment 3.

Fig. 10 is a schematic diagram showing the structure of the dehumidifier of embodiment 4.

Fig. 11 is a schematic diagram showing the structure of the dehumidifier of embodiment 5.

Fig. 12 is a cross-sectional view of the evaporator, the 1 st condensation unit, the 2 nd condensation unit, and the 3 rd condensation unit of the dehumidifier of embodiment 5.

Detailed Description

Hereinafter, embodiments will be described with reference to the drawings. In the drawings, the same or corresponding portions are denoted by the same reference numerals, and the description thereof will not be repeated.

Embodiment 1.

The configuration of the dehumidifier 1 according to embodiment 1 will be described with reference to fig. 1 and 2. Fig. 1 is a refrigerant circuit diagram of a dehumidifying apparatus 1 of embodiment 1. Fig. 2 is a schematic diagram showing the structure of the dehumidifier 1 according to embodiment 1.

As shown in fig. 1 and 2, the dehumidification device 1 includes a refrigerant circuit 10, a blower 6, and a housing 20, and the refrigerant circuit 10 includes a compressor 2, a condenser 3, a pressure reducing device 4, and an evaporator 5. The refrigerant circuit 10 and the blower 6 are disposed in the casing 20. The housing 20 faces an external space (indoor space) that is a dehumidifying object of the dehumidifying apparatus 1.

The refrigerant circuit 10 is configured to circulate the refrigerant in the order of the compressor 2, the condenser 3, the pressure reducing device 4, and the evaporator 5. Specifically, the refrigerant circuit 10 is configured by sequentially connecting the compressor 2, the condenser 3, the pressure reducing device 4, and the evaporator 5 via pipes. The refrigerant passes through the piping and circulates through the refrigerant circuit 10 in the order of the compressor 2, the condenser 3, the pressure reducing device 4, and the evaporator 5.

The compressor 2 is configured to compress a refrigerant. Specifically, the compressor 2 is configured to suck and compress a low-pressure refrigerant from a suction port, and to discharge the refrigerant as a high-pressure refrigerant from a discharge port. The compressor 2 may be configured to have a variable discharge capacity of the refrigerant. Specifically, the compressor 2 may be a variable frequency compressor. When the discharge capacity of the compressor 2 is variable, the discharge capacity of the compressor 2 can be adjusted to control the refrigerant circulation amount in the dehumidifier 1.

The condenser 3 is configured to condense and cool the refrigerant boosted by the compressor 2. The condenser 3 is a heat exchanger that exchanges heat between refrigerant and air. The condenser 3 has refrigerant inlets and outlets, and air inlets and outlets. The refrigerant inlet of the condenser 3 is connected to the discharge port of the compressor 2 through a pipe. The heat transfer tube of the condenser 3 is a round tube.

The condenser 3 includes a1 st condensation portion 3a and a2 nd condensation portion 3b. The condenser 3 is configured such that the refrigerant flows in the order of the 2 nd condensation unit 3b and the 1 st condensation unit 3a. The 1 st condensation unit 3a is connected to the 2 nd condensation unit 3b. The 2 nd condensing unit 3b is configured to condense and cool the refrigerant boosted by the compressor 2. The 2 nd condensing unit 3b is a heat exchanger that exchanges heat between the refrigerant and air. The 2 nd condensing portion 3b has a refrigerant inlet and outlet, and an air inlet and outlet. In the present embodiment, the refrigerant inlet of the 2 nd condensation unit 3b is connected to the discharge port of the compressor 2 through a pipe. The 2 nd condensing portion 3b is disposed downstream of the 1 st condensing portion 3a in the air flow generated by the blower 6. That is, the 2 nd condensation unit 3b is disposed downstream of the 1 st condensation unit 3a. The height of the 2 nd condensation part 3b is higher than the height of the 1 st condensation part 3a. The height of the 2 nd condensing portion 3b is equal to the height of the evaporator 5. This ensures a heat transfer area of the 2 nd condensation unit 3b and allows the same air volume to pass through the 2 nd condensation unit 3b as the air volume passing through the evaporator 5. In addition, in the direction in which the 2 nd condensation portion 3b faces the evaporator 5, the 2 nd condensation portion 3b is disposed so as to overlap the evaporator 5.

The 1 st condensation unit 3a is configured to further condense and cool the refrigerant cooled by the 2 nd condensation unit 3b. The 1 st condensation unit 3a is a heat exchanger that exchanges heat between the refrigerant and air. The 1 st condensation portion 3a has a refrigerant inlet and outlet, and an air inlet and outlet. In the present embodiment, the refrigerant inlet of the 1 st condensation unit 3a is connected to the outlet of the 2 nd condensation unit 3b by piping. The 1 st condensation unit 3a is disposed upstream of the 2 nd condensation unit 3b in the air flow generated by the blower 6. That is, the 1 st condensation unit 3a is disposed upstream of the 2 nd condensation unit 3b. The 1 st condensation unit 3a is disposed downstream of the evaporator 5 in the air flow generated by the blower 6. That is, the 1 st condensation unit 3a is disposed downstream of the evaporator 5. The 1 st condensation section 3a has a height lower than that of the evaporator 5.

The decompression device 4 is configured to decompress and expand the refrigerant cooled by the condenser 3. The pressure reducing device 4 is, for example, an expansion valve. The expansion valve may also be an electronically controlled valve. The pressure reducing device 4 is not limited to an expansion valve, and may be a capillary tube. The pressure reducing device 4 is connected to a refrigerant outlet of the condenser 3 and a refrigerant inlet of the evaporator 5 through pipes.

The evaporator 5 is configured to absorb heat from the refrigerant decompressed and expanded by the decompression device 4 to evaporate the refrigerant. The evaporator 5 is a heat exchanger that exchanges heat between refrigerant and air. The evaporator 5 has refrigerant inlets and outlets, and air inlets and outlets. The refrigerant outlet of the evaporator 5 is connected to the suction port of the compressor 2 through a pipe. The evaporator 5 is disposed upstream of the condenser 3 in the air flow generated by the blower 6. That is, the evaporator 5 is disposed upstream of the condenser 3. Specifically, the evaporator 5 is disposed upstream of the 1 st condensation unit 3a. The heat transfer tube of the evaporator 5 is a circular tube.

In the present embodiment, the refrigerant circuit 10 is configured to circulate the refrigerant in the order of the compressor 2, the 2 nd condensation unit 3b, the 1 st condensation unit 3a, the pressure reducing device 4, and the evaporator 5.

The blower 6 is configured to send out air. The blower 6 is configured to take in air from the outside of the casing 20 to the inside and send it out to the condenser 3 and the evaporator 5. Specifically, the blower 6 is configured to take in air from an external space (indoor space) into the casing 20, to send a part of the air to the evaporator 5, the 1 st condensation unit 3a, and the 2 nd condensation unit 3b, and to send another part of the air to the evaporator 5, the 2 nd condensation unit 3b without passing through the 1 st condensation unit 3a. The blower 6 is configured to discharge the air having passed through the 2 nd condensation unit 3b to the outside of the casing 20.

In the present embodiment, the blower 6 includes a shaft 6a and a fan 6b, and the fan 6b rotates around the shaft 6 a. By rotating the fan 6B around the shaft 6a, the air taken in from the external space (indoor space) as indicated by an arrow a in the figure passes through the evaporator 5, the 1 st condensation unit 3a, and the 2 nd condensation unit 3B in this order as indicated by an arrow B in the figure, and is then discharged again to the external space (indoor space) as indicated by an arrow C in the figure. By rotating the fan 6B around the shaft 6a, the air taken in from the external space (indoor space) as indicated by arrow a in the figure passes through the evaporator 5 and the 2 nd condensation unit 3B in this order without passing through the 1 st condensation unit 3a as indicated by arrow B' in the figure, and is then discharged again to the external space (indoor space) as indicated by arrow C in the figure. In this way, the air circulates in the external space (indoor space) via the dehumidifying apparatus 1.

The casing 20 is provided with a suction port 21 for allowing air to enter the casing 20 from an external space (indoor space) to be dehumidified, and a blowout port 22 for blowing out air from the inside of the casing 20 to the external space (indoor space). The casing 20 further includes an air passage (air passage) 23, and the air passage (air passage) 23 connects the suction port 21 and the blowout port 22. The evaporator 5, the condenser 3, and the blower 6 are disposed in the air passage 23. Therefore, the evaporator 5 and the condenser 3 are disposed in the same air passage 23. The evaporator 5, the 1 st condensation unit 3a, and the 2 nd condensation unit 3b are disposed in the air passage 23 in the order of the evaporator 5, the 1 st condensation unit 3a, and the 2 nd condensation unit 3b from upstream to downstream in the air flow.

In the air duct 23, a part of the air sucked into the casing 20 from the outside of the casing 20 through the suction port 21 passes through the evaporator 5, the 1 st condensation unit 3a, and the 2 nd condensation unit 3b in this order, and is blown out of the casing 20 through the outlet port 22. The other part of the air sucked into the casing 20 from the outside of the casing 20 through the suction port 21 passes through the evaporator 5 and the 2 nd condensation unit 3b in this order without passing through the 1 st condensation unit 3a, and is blown out of the casing 20 through the outlet port 22.

In the dehumidifier 1, components constituting the refrigerant circuit may be disposed in the air passage 23 in addition to the condenser 3, the evaporator 5, and the blower 6. For example, the pressure reducing device 4 may be disposed in the air duct 23.

In the case where the air conditioner is installed indoors, the heat of the condenser 3 may be dissipated outdoors to cool the indoor space. For heat dissipation to the outside, the exhaust duct may be mounted on the equipment, and the equipment itself may be provided on the window side.

Next, the configuration of the evaporator 5, the 1 st condensation unit 3a, and the 2 nd condensation unit 3b will be described in detail with reference to fig. 3. Fig. 3 is a cross-sectional view of evaporator 5, 1 st condensation unit 3a, and 2 nd condensation unit 3b according to embodiment 1. In fig. 3, for convenience of explanation, the evaporator 5, the 1 st condensation unit 3a, and a part of the upper side of the 2 nd condensation unit 3b are illustrated.

In the dehumidifying apparatus 1 of the present embodiment, the 1 st condensation unit 3a has a plurality of fins 11 and heat transfer tubes 12. The plurality of fins 11 are each formed in a thin plate shape. The plurality of fins 11 are arranged to be stacked on each other. The heat transfer pipe 12 is configured as a plurality of fins 11 stacked through each other in the stacking direction. The heat transfer pipe 12 has: a plurality of linear portions extending linearly in the stacking direction; and a plurality of curved portions connecting the plurality of straight portions. The heat transfer pipe 12 is constructed to meander by connecting each of the plurality of straight portions and each of the plurality of bent portions in series with each other. The heat transfer pipe 12 is configured to flow a refrigerant. The heat transfer pipe 12 is a circular pipe.

In the dehumidifying device 1 of the present embodiment, the 2 nd condensing portion 3b has a plurality of fins 13 and heat transfer tubes 14. The plurality of fins 13 are each formed in a thin plate shape. The plurality of fins 13 are arranged to be stacked on each other. The heat transfer pipe 14 is configured as a plurality of fins 13 stacked through each other in the stacking direction. The heat transfer pipe 14 has: a plurality of linear portions extending linearly in the stacking direction; and a plurality of curved portions connecting the plurality of straight portions. The heat transfer pipe 14 is constructed to meander by connecting each of the plurality of straight portions and each of the plurality of bent portions in series with each other. The heat transfer pipe 14 is configured to flow a refrigerant. The heat transfer pipe 14 is a circular pipe.

In the dehumidifying device 1 of the present embodiment, the evaporator 5 has a plurality of fins 15 and heat transfer tubes 16. The plurality of fins 15 are each formed in a thin plate shape. The plurality of fins 15 are arranged to be stacked on each other. The heat transfer pipe 16 is configured to penetrate the plurality of fins 15 stacked one on another in the stacking direction. The heat transfer pipe 16 has: a plurality of linear portions extending linearly in the stacking direction; and a plurality of curved portions connecting the plurality of straight portions. The heat transfer pipe 16 is configured to meander by connecting each of the plurality of straight portions and each of the plurality of straight portions in series with each other. The heat transfer pipe 16 is a circular pipe.

Fig. 3 is a cross-sectional view of a cross section perpendicular to the stacking direction of the plurality of fins 11 of the 1 st condensation portion 3a, the plurality of fins 13 of the 2 nd condensation portion 3b, and the plurality of fins 15 of the evaporator 5, respectively. In the 1 st condensation portion 3a, a plurality of straight portions of the heat transfer tubes 12 are arranged in the cross section shown in fig. 3. The outer diameter and the inner diameter of the straight portions of the plurality of heat transfer pipes 12 may be the same as each other.

In the present embodiment, the linear portions of the plurality of heat transfer tubes 12 are arranged in 2 rows in the column direction. The intervals between the straight portions of the heat transfer tubes 12 arranged in each of the 2 columns in the column direction may be the same as each other. The interval is a distance between centers of straight portions of the heat transfer tubes 12 arranged in the adjacent columns in the column direction. In the present embodiment, the straight portions of the plurality of heat transfer tubes 12 of each column adjacent to each other in the column direction are arranged so as to be offset from each other in the segment direction. That is, the centers of the straight portions of the plurality of heat transfer tubes 12 of each column adjacent to each other in the column direction are not arranged in a straight line in the column direction.

Further, in the present embodiment, the straight portions of the plurality of heat transfer tubes 12 of each column adjacent to each other in the column direction are arranged so as not to overlap each other in the column direction. Further, in the present embodiment, the straight portions of the plurality of heat transfer tubes 12 of each column adjacent to each other in the column direction are arranged so as not to overlap each other in the segment direction.

In the present embodiment, the linear portions of the plurality of heat transfer tubes 12 are arranged in the row in the segment direction to be 2 or more segments. In the present embodiment, the linear portions of the plurality of heat transfer tubes 12 are arranged in a linear manner in the segment direction in each row. That is, the centers of the straight portions of the plurality of heat transfer tubes 12 arranged in the segment direction in each column are arranged in a straight line. In the present embodiment, the positions in the segment direction of the straight portions of the plurality of heat transfer tubes 12 arranged in each of the 2 columns are arranged at the center between the positions in the segment direction of the straight portions of the plurality of heat transfer tubes 12 arranged in the adjacent columns. In the present embodiment, the number of the plurality of heat transfer pipes 12 in the segment direction of at least 1 row is at least 1 less than the number of the plurality of heat transfer pipes 16 in the segment direction.

In the 2 nd condensation portion 3b, in the cross section shown in fig. 3, straight portions of the plurality of heat transfer tubes 14 are arranged. The outer diameter and the inner diameter of the straight portions of the plurality of heat transfer pipes 14 may be the same as each other.

In the present embodiment, the linear portions of the plurality of heat transfer tubes 14 are arranged in 2 rows in the column direction. The intervals between the straight portions of the heat transfer tubes 14 arranged in the respective columns in the column direction of these 2 columns may be the same as each other. The interval is a distance between centers of straight portions of the heat transfer tubes 14 arranged in the adjacent columns in the column direction. In the present embodiment, the straight portions of the plurality of heat transfer tubes 14 of each column adjacent to each other in the column direction are arranged so as to be offset from each other in the segment direction. That is, the centers of the straight portions of the plurality of heat transfer tubes 14 of each column adjacent to each other in the column direction are not arranged in a straight line in the column direction.

Further, in the present embodiment, the straight portions of the plurality of heat transfer tubes 14 of each column adjacent to each other in the column direction are arranged so as not to overlap each other in the column direction. Further, in the present embodiment, the straight portions of the plurality of heat transfer tubes 14 of each column adjacent to each other in the column direction are arranged so as not to overlap each other in the segment direction.

In the present embodiment, the linear portions of the plurality of heat transfer tubes 14 are arranged in the row in the segment direction to be 3 or more segments. In the present embodiment, the linear portions of the plurality of heat transfer tubes 14 are arranged in a linear manner in the segment direction in each row. That is, the centers of the straight portions of the plurality of heat transfer tubes 14 arranged in the segment direction in each column are arranged in a straight line. In the present embodiment, the positions in the segment direction of the straight portions of the plurality of heat transfer tubes 14 arranged in each of the 2 columns are arranged at the center between the positions in the segment direction of the straight portions of the plurality of heat transfer tubes 14 arranged in the adjacent columns.

In the evaporator 5, in the cross section shown in fig. 3, straight portions of a plurality of heat transfer tubes 16 are arranged. The outer diameter and the inner diameter of the straight portions of the plurality of heat transfer pipes 16 may be the same as each other.

In the present embodiment, the linear portions of the plurality of heat transfer tubes 16 are arranged in 3 columns in the column direction. The intervals between the straight portions of the heat transfer tubes 16 arranged in the respective columns in the column direction of these 3 columns may be the same as each other. The interval is a distance between centers of straight portions of the heat transfer tubes 16 arranged in adjacent columns in the column direction. In the present embodiment, the straight portions of the plurality of heat transfer tubes 16 of each column adjacent to each other in the column direction are arranged so as to be offset from each other in the segment direction. That is, the centers of the 2 nd straight portions of the plurality of heat transfer tubes 16 of each row adjacent to each other in the row direction are not arranged in a straight line in the row direction.

Further, in the present embodiment, the straight portions of the plurality of heat transfer tubes 16 of each column adjacent to each other in the column direction are arranged so as not to overlap each other in the column direction. Further, in the present embodiment, the straight portions of the plurality of heat transfer tubes 16 of each column adjacent to each other in the column direction are arranged so as not to partially overlap each other in the segment direction.

In the present embodiment, the linear portions of the plurality of heat transfer tubes 16 are arranged in the row in the segment direction to be 3 or more segments. In the present embodiment, the linear portions of the plurality of heat transfer tubes 16 are arranged in a linear manner in the segment direction in each row. That is, the centers of the straight portions of the plurality of heat transfer tubes 16 arranged in the segment direction in each column are arranged in a straight line. In the present embodiment, the positions in the segment direction of the straight portions of the plurality of heat transfer tubes 16 arranged in each of the columns at both ends in the column direction of the 3 columns are identical to each other. Further, the positions in the segment direction of the straight portions of the heat transfer tubes 16 arranged in the center of the 3 columns in the column direction are arranged in the center between the positions in the segment direction of the straight portions of the plurality of heat transfer tubes 16 arranged in the respective columns at both ends.

The evaporator 5, the 1 st condensation unit 3a, and the 2 nd condensation unit 3b may be a multi-path heat exchanger having a plurality of refrigerant paths.

The heat transfer tubes 12, 14, and 16 are not limited to round tubes, and may be flat tubes. By using flat tubes having a higher heat conductivity than round tubes, the amount of heat exchange in each heat exchanger can be increased. In addition, ventilation resistance can be reduced.

Next, the operation of the dehumidifying apparatus 1 according to embodiment 1 in the dehumidifying operation will be described with reference to fig. 1 and 2.

The superheated gas refrigerant discharged from the compressor 2 flows into the 2 nd condensation portion 3b disposed in the air passage 23. The superheated gas refrigerant flowing into the 2 nd condensation unit 3b exchanges heat with air flowing into the air passage 23 from the outside space through the suction port 21 and passing through the evaporator 5 disposed in the air passage 23, and is cooled. Then, the refrigerant is cooled by heat exchange with air flowing into the air passage 23 from the outside space through the suction port 21 and passing through the evaporator 5 and the 1 st condensation unit 3a disposed in the air passage 23, and becomes a refrigerant in a gas-liquid two-phase state.

On the other hand, a part of the air passing through the 2 nd condensation unit 3b disposed in the air duct 23 passes through the evaporator 5 also disposed in the air duct 23, and then is heat-exchanged with the superheated gas-state refrigerant or the gas-liquid two-phase-state refrigerant in the 2 nd condensation unit 3b to be heated. The other part of the air passing through the 2 nd condensation unit 3b disposed in the air duct 23 passes through the evaporator 5 and the 1 st condensation unit 3a also disposed in the air duct 23, and then is heat-exchanged with the superheated gas-state refrigerant or the gas-liquid two-phase-state refrigerant in the 2 nd condensation unit 3b to be heated.

The refrigerant in a gas-liquid two-phase state flowing out of the 2 nd condensation unit 3b flows into the 1 st condensation unit 3a. The refrigerant in the gas-liquid two-phase state flowing into the 1 st condensation unit 3a is further cooled by heat exchange with the air passing through the evaporator 5 disposed in the air passage 23, and becomes a supercooled liquid state refrigerant.

On the other hand, the air passing through the 1 st condensation unit 3a disposed in the air duct 23 passes through the evaporator 5 similarly disposed in the air duct 23, and then is heated by heat exchange with the refrigerant in the gas-liquid two-phase state in the 1 st condensation unit 3a.

The supercooled liquid refrigerant flowing out of the 1 st condensation portion 3a is decompressed by the decompressing device 4 and becomes a gas-liquid two-phase refrigerant, and then flows into the evaporator 5 disposed in the air passage 23. The refrigerant in the gas-liquid two-phase state flowing into the evaporator 5 is heated by heat exchange with the air taken into the air passage 23 from the outside space through the suction port 21, and becomes a refrigerant in the superheated gas state. The refrigerant in the superheated gas state is sucked into the compressor 2, compressed by the compressor 2, and discharged again.

On the other hand, the air passing through the evaporator 5 disposed in the air passage 23 is taken into the air passage 23 from the outside space through the suction port 21, and then, is subjected to heat exchange with the refrigerant in the gas-liquid two-phase state in the evaporator 5, cooled to a temperature equal to or lower than the dew point of the air, and dehumidified.

Next, the operational effects of the dehumidifier 1 of embodiment 1 will be described in comparison with the comparative example.

Fig. 4 is a sectional view of the evaporator 5 and the condenser 3 of the dehumidifying apparatus 1 of the comparative example. In general, in order to improve the performance of the condenser 3, it is necessary to increase the heat transfer area. In order to increase the heat transfer area, it is considered to use a plurality of condensers 3. In the comparative example, the condenser 3 includes a1 st condensation portion 3a on the upwind side and a2 nd condensation portion 3b on the downwind side. The 1 st condensation unit 3a, the 2 nd condensation unit 3b and the evaporator 5 have the same height. Therefore, in the dehumidifying apparatus 1 of the comparative example, all of the air passing through the evaporator 5 passes through the 1 st condensation portion 3a and then flows into the 2 nd condensation portion 3b. Therefore, in the dehumidifier 1 of the comparative example, the air having a relatively low temperature having passed through the evaporator 5 cannot flow into the 2 nd condensation unit 3b without passing through the 1 st condensation unit 3a. In the dehumidifier 1 of the comparative example, the internal volume of the condenser 3 increases, and it is difficult to achieve the supercooling degree. Therefore, in the dehumidifying apparatus 1 of the comparative example, the amount of refrigerant needs to be increased.

According to the dehumidifying apparatus 1 of the present embodiment, the 1 st condensation part 3a is lower in height than the evaporator 5, and the 2 nd condensation part 3b is higher in height than the 1 st condensation part 3a. Therefore, a part of the air having a relatively low temperature having passed through the evaporator 5 can be made to flow into the 2 nd condensation portion 3b without passing through the 1 st condensation portion 3a. This allows the air having a low temperature passing through the evaporator 5 to exchange heat with the refrigerant having a high temperature flowing from the compressor 2 into the 2 nd condensation portion 3b. Therefore, by bringing the air having passed through the evaporator 5 at a relatively low temperature into contact with the 2 nd condensation portion 3b through which the refrigerant in the superheated gaseous state passes, the temperature difference between the refrigerant and the air can be increased. This can increase the heat exchange amount of the 2 nd condensation unit 3b, and thus the heat exchange amount of the condenser 3 can be increased.

Fig. 5 is a diagram showing a relationship between the amount of refrigerant and the amount of dehumidification based on the change in the height of the 1 st condensation unit 3a, that is, the change in the number of stages. The amount of refrigerant is the amount of refrigerant enclosed in the refrigerant circuit 10. The number of stages of the evaporator 5 is equal to the number of stages of the 1 st condensation unit 3a in the conventional dehumidification device, and the number of stages of the 1 st condensation unit 3a is A0. The number of stages of the 1 st condensation part 3a of the dehumidifying apparatus, which is appropriately reduced from the number of stages A0, is A1. The appropriate reduction of the number of stages means that the number of stages is reduced in a range where the degree of supercooling increases, the temperature of the refrigerant at the outlet of the 1 st condensation portion 3a decreases, and the amount of dehumidification increases by increasing the density of the refrigerant by reducing the internal volume of the 1 st condensation portion 3a. The number of stages of the 1 st condensation part 3a, which is excessively reduced in the number of stages compared with the number of stages A0, is the number of stages A2. The excessively reduced number of stages means that the effect of reducing the number of stages until the heat transfer area is reduced is greater than the effect of reducing the internal volume of the 1 st condensation unit 3a, and the temperature of the refrigerant at the outlet of the 1 st condensation unit 3a is increased and the amount of dehumidification is reduced.

When the number of stages of the 1 st condensation unit 3a is reduced to the number of stages A1, the internal volume of the 1 st condensation unit 3a is reduced, and therefore the refrigerant density in the 1 st condensation unit 3a can be increased. Therefore, the degree of supercooling can be increased, and the enthalpy difference between the front and rear of the evaporator can be increased. Thus, the maximum dehumidification amount of the dehumidification device of the number of stages A1 is reduced when the amount of refrigerant is optimal, as compared with the conventional dehumidification device of the number of stages A0, but the dehumidification amount can be increased compared with the conventional dehumidification device when the amount of refrigerant is smaller. This can reduce the amount of refrigerant. However, when the number of stages of the 1 st condensation unit 3a is reduced to the number of stages A2, the influence of the reduction in the heat exchange amount caused by the reduction in the heat transfer area of the 1 st condensation unit 3a including the fins 11 and the heat transfer tubes 12 becomes large. As a result, the amount of dehumidification is reduced as a whole, and thus the target amount of dehumidification cannot be achieved. Therefore, it is necessary to select the optimum number of stages A1, in which the number of stages A2 < the number of stages A1 < the number of stages A0, which corresponds to the target dehumidification amount.

Further, by reducing the amount of refrigerant, the proportion of liquid refrigerant at the time of stopping the operation of the dehumidifier 1 can be reduced. This prevents a large amount of liquid refrigerant from flowing into the compressor 2 when the operation is started. This ensures the quality of the compressor 2.

Further, by reducing the number of stages of the 1 st condensation portion 3a, the ventilation resistance of the 1 st condensation portion 3a is reduced, and thus the fan input of the blower 6 can be reduced.

Further, by reducing the number of stages of the 1 st condensation unit 3a, the material cost of the 1 st condensation unit 3a can be reduced.

Embodiment 2.

Referring to fig. 6, a dehumidifying device 1 according to embodiment 2 will be described. The dehumidifying apparatus 1 of the present embodiment is different from the dehumidifying apparatus 1 of embodiment 1 in that it includes a1 st partition 8a, a1 st air passage 23a, and a2 nd air passage 23 b.

In the dehumidifying device 1 of the present embodiment, the housing 20 has: a suction port 21 for taking in air; a1 st air passage 23a and a2 nd air passage 23b which communicate with the suction port 21; and a1 st partition 8a. In the 1 st air passage 23a, an evaporator 5, a1 st condensation unit 3a, a2 nd condensation unit 3b, and a blower 6 are disposed in the air flow from upstream to downstream. In the 2 nd air passage 23b, the evaporator 5, the 2 nd condensing unit 3b, and the blower 6 are disposed in the air flow from upstream to downstream.

In the 1 st air passage 23a, a part of the air sucked into the casing 20 from the outside of the casing 20 through the suction port 21 passes through the evaporator 5, the 1 st condensation unit 3a, and the 2 nd condensation unit 3b in this order, and is blown out of the casing 20 through the blowing port 22. In the 2 nd air passage 23b, the other part of the air sucked into the casing 20 from the outside of the casing 20 through the suction port 21 passes through the evaporator 5 and the 2 nd condensation portion 3b in this order without passing through the 1 st condensation portion 3a, and is blown out of the casing 20 through the outlet port 22.

The 1 st air passage 23a is separated from the 2 nd air passage 23 b. The 1 st air passage 23a and the 2 nd air passage 23b are partitioned by the 1 st partition 8a. The 1 st air passage 23a and the 2 nd air passage 23b are formed by the casing 20 and the 1 st partition 8a, respectively. In the flow direction of the air in the 2 nd air passage 23b, one end of the 1 st partition 8a located upstream is formed at least upstream of the center of the fin 11 (see fig. 3). The other end of the 1 st partition 8a located downstream in the flow direction of the air in the 2 nd air passage 23b is formed at a position downstream of at least the center of the fin 11 (see fig. 3). Preferably, in the flow direction of the air in the 2 nd air duct 23b, one end of the 1 st partition 8a located on the upstream side is formed at the air inlet of the 1 st condensation unit 3a or at a position upstream of the air inlet. Preferably, the other end of the 1 st partition 8a located downstream in the flow direction of the air in the 2 nd air passage 23b is formed at the air outlet of the 1 st condensation unit 3a or at a position downstream of the air outlet. Preferably, one end of the 1 st partition 8a on the upstream side in the flow direction of the air in the 2 nd air passage 23b is in contact with the air outlet of the evaporator 5. Preferably, the other end of the 1 st partition 8a on the downstream side in the flow direction of the air in the 2 nd air duct 23b is in contact with the air inlet of the 2 nd condensation unit 3b. The 1 st partition 8a is formed in a flat plate shape, for example. The 1 st partition 8a is fixed to the inside of the housing 20.

According to the dehumidifying apparatus 1 of the present embodiment, the 1 st air passage 23a and the 2 nd air passage 23b are partitioned by the 1 st partition 8a. Therefore, the temperature of the air passing through the 1 st condensation unit 3a in the 1 st air passage 23a can be prevented from being increased by mixing with the air passing through the evaporator 5 in the 2 nd air passage 23a at a relatively low temperature, and the temperature of the air passing through the evaporator 5 in the 2 nd air passage 23a can be prevented from being increased.

The material constituting the 1 st partition 8a may be a material having a lower thermal conductivity than the material constituting the heat transfer tube and the fins of the 1 st condensation unit 3a through which the refrigerant flows. This can reduce the heat exchange between the air in the 1 st air passage 23a and the air in the 2 nd air passage 23b by the 1 st partition 8a.

Embodiment 3.

The dehumidifying apparatus 1 according to embodiment 3 will be described with reference to fig. 7 to 9. The dehumidifying apparatus 1 of the present embodiment is different from the dehumidifying apparatus 1 of embodiment 1 in that the dehumidifying apparatus is provided with a 3 rd condensing unit 3c.

Referring to fig. 7 and 8, in the dehumidifying apparatus 1 of the present embodiment, the condenser 3 includes a 3 rd condensing portion 3c. The 3 rd condensation unit 3c is disposed between the compressor 2 and the 2 nd condensation unit 3b in the refrigerant circuit 10. The refrigerant circuit 10 is configured to circulate the refrigerant in the order of the compressor 2, the 3 rd condensation unit 3c, the 2 nd condensation unit 3b, the 1 st condensation unit 3a, the pressure reducing device 4, and the evaporator 5. The 3 rd condensing unit 3c is disposed above the 2 nd condensing unit 3b. The 3 rd condensing portion 3c is higher than the evaporator 5.

The 3 rd condensing unit 3c is configured to condense and cool the refrigerant boosted by the compressor 2. The 3 rd condensing unit 3c is a heat exchanger that exchanges heat between the refrigerant and the air. The 3 rd condensing portion 3c has a plurality of fins 17 and heat transfer tubes 18. The 3 rd condensing portion 3c has a refrigerant inlet and outlet, and an air inlet and outlet. The refrigerant inlet and outlet of the 3 rd condensation unit 3c are connected to the discharge port of the compressor 2 and the refrigerant inlet of the 2 nd condensation unit 3b, respectively, by piping.

Referring to fig. 9, in the present embodiment, the 3 rd condensing unit 3c is a heat exchanger having fins and heat transfer tubes having the same shape as the 2 nd condensing unit 3b. The 3 rd condensing portion 3c is located above the 2 nd condensing portion 3b in the segment direction. That is, the straight portions of the heat transfer tubes 18 of the 3 rd condensation unit 3c and the heat transfer tubes 14 of the 2 nd condensation unit 3b are arranged in a straight line in the segment direction. The heat transfer tube 18 is not limited to a round tube, and may be a flat tube.

In the air duct 23, a part of the air sucked into the casing 20 from the outside of the casing 20 through the suction port 21 passes through the evaporator 5, the 1 st condensation unit 3a, and the 2 nd condensation unit 3b in this order, and is blown out of the casing 20 through the outlet port 22. The other part of the air sucked into the casing 20 from the outside of the casing 20 through the suction port 21 passes through the evaporator 5 and the 2 nd condensation unit 3b in this order without passing through the 1 st condensation unit 3a, and is blown out of the casing 20 through the outlet port 22. The other part of the air sucked into the casing 20 from the outside of the casing 20 through the suction port 21 passes through the 3 rd condensation part 3c without passing through the evaporator 5 and the 1 st condensation part 3a, and is blown out of the casing 20 through the blowing port 22.

In the present embodiment, by rotating the fan 6B about the shaft 6a, air taken in from the outside space (indoor space) as indicated by arrow a in the figure flows in the air passage 23 as indicated by arrow B, B' in the figure, and flows as indicated by arrow b″ in the figure. The air shown by arrow B, B' B "in the drawing is mixed with each other and discharged to the outside space (indoor space) of the casing 20 through the air outlet 22.

According to the dehumidifying apparatus 1 of the present embodiment, the height of the 3 rd condensing portion 3c is higher than the height of the evaporator 5. Therefore, the volume of air flowing through the entire condenser 3 including the 1 st condensation unit 3a, the 2 nd condensation unit 3b, and the 3 rd condensation unit 3c can be made larger than the volume of air flowing through the evaporator 5. By increasing the air volume of the condenser 3 as a whole, the heat transfer performance on the condenser 3 side can be improved, and therefore the condensing temperature of the refrigerant can be reduced. Further, by lowering the condensation temperature, the difference between the condensation pressure and the evaporation pressure in the refrigerant circuit can be reduced, and thus the input in the compressor 2 can be reduced. This can increase the EF (Energy Factor) value.

Embodiment 4.

Referring to fig. 10, a dehumidifying apparatus 1 according to embodiment 4 will be described. The dehumidifying apparatus 1 of the present embodiment is different from the dehumidifying apparatus 1 of embodiment 3 in that it includes a1 st partition 8a, a2 nd partition 8b, a1 st suction 21a, a2 nd suction 21b, a1 st air path 23a, a2 nd air path 23b, and a 3 rd air path 23c.

The air duct 23 includes a1 st air duct 23a, a2 nd air duct 23b, and a 3 rd air duct 23c. The suction port 21 includes a1 st suction portion 21a and a2 nd suction portion 21b. The 1 st air passage 23a and the 2 nd air passage 23b are configured to connect the 1 st suction portion 21a and the air outlet 22. The 3 rd air passage 23c connects the 2 nd suction portion 21b and the air outlet 22. The 1 st suction portion 21a communicates with the 1 st air passage 23a and the 2 nd air passage 23 b. The 2 nd suction portion 21b communicates with the 3 rd air passage 23c. The 3 rd condensation unit 3c is disposed in the 3 rd air passage 23c so that the air taken in from the 2 nd suction unit 21b flows.

In the dehumidifying device 1 of the present embodiment, the housing 20 has: a suction port 21 for taking in air; a1 st air passage 23a, a2 nd air passage 23b, and a 3 rd air passage 23c, which communicate with the suction port 21; and 1 st and 2 nd partitions 8a and 8b. In the 1 st air passage 23a, an evaporator 5, a1 st condensation unit 3a, a2 nd condensation unit 3b, and a blower 6 are disposed in the air flow from upstream to downstream. The evaporator 5, the 1 st condensation unit 3a, and the 2 nd condensation unit 3b are disposed in the 1 st air path 23a so that the air taken in from the intake port 21 flows in the order of the evaporator 5, the 1 st condensation unit 3a, and the 2 nd condensation unit 3b. In the 2 nd air passage 23b, an evaporator 5, a2 nd condensing unit 3b, and a blower 6 are disposed in the air flow from upstream to downstream. The evaporator 5 and the 2 nd condensing unit 3b are disposed in the 2 nd air duct 23b so that the air taken in from the intake port 21 flows in the order of the evaporator 5 and the 2 nd condensing unit 3b. In the 3 rd air passage 23c, the 3 rd condensation unit 3c and the blower 6 are disposed in the air flow from upstream to downstream. The 3 rd condensation unit 3c is disposed in the 3 rd air passage 23c so as to allow the air taken in from the intake port 21 to flow therethrough.

In the 1 st air passage 23a, a part of the air sucked into the casing 20 from the outside of the casing 20 through the suction port 21 passes through the evaporator 5, the 1 st condensation unit 3a, and the 2 nd condensation unit 3b in this order, and is blown out of the casing 20 through the blowing port 22. In the 2 nd air passage 23b, the other part of the air sucked into the casing 20 from the outside of the casing 20 through the suction port 21 passes through the evaporator 5 and the 2 nd condensation portion 3b in this order without passing through the 1 st condensation portion 3a, and is blown out of the casing 20 through the outlet port 22. In the 3 rd air passage 23c, the other part of the air sucked into the casing 20 from the outside of the casing 20 through the suction port 21 passes through the 3 rd condensation unit 3c and is blown out of the casing 20 through the air outlet 22.

The 1 st air passage 23a is separated from the 2 nd air passage 23 b. The 1 st air passage 23a and the 2 nd air passage 23b are partitioned by the 1 st partition 8a. The 1 st air passage 23a and the 2 nd air passage 23b are formed by the casing 20 and the 1 st partition 8a, respectively. In the flow direction of the air in the 2 nd air passage 23b, one end of the 1 st partition 8a located upstream is formed at least upstream of the center of the fin 11 (see fig. 3). In the flow direction, the other end of the 1 st partition 8a located downstream is formed at least downstream of the center of the fin 11 (see fig. 3).

The 2 nd air passage 23b is separated from the 3 rd air passage 23c. The 2 nd air passage 23b and the 3 rd air passage 23c are partitioned by the 2 nd partition 8b. The 2 nd and 3 rd air passages 23b and 23c are formed by the casing 20 and the 2 nd partition 8b, respectively. In the flow direction of the air in the 3 rd air passage 23c, one end of the 2 nd partition 8b located on the upstream side is formed at least on the upstream side of the air outlet of the evaporator 5. In the flow direction, the other end of the 2 nd partition 8b located downstream is formed at a position at least downstream of the air inlet of the 1 st condensation unit 3a. Preferably, in the flow direction, one end of the 2 nd partition 8b located on the upstream side is formed on the upstream side of the air inlet of the evaporator 5. Preferably, in the flow direction, the other end of the 2 nd partition 8b located downstream is formed downstream of the air outlet of the 1 st condensation unit 3a. The 1 st partition 8a and the 2 nd partition 8b are formed in a flat plate shape, for example. The 1 st partition 8a and the 2 nd partition 8b are fixed to the inside of the housing 20.

According to the dehumidifying apparatus 1 of the present embodiment, the 1 st air passage 23a and the 2 nd air passage 23b are partitioned by the 1 st partition 8a. Therefore, the temperature of the air passing through the 1 st condensation unit 3a in the 1 st air passage 23a and the temperature of the air passing through the evaporator 5 in the 2 nd air passage 23b can be prevented from being mixed with each other, and the temperature of the air passing through the evaporator 5 in the 2 nd air passage 23b can be prevented from being increased. The 2 nd air passage 23b and the 3 rd air passage 23c are partitioned by the 2 nd partition 8b. Therefore, the temperature of the air having passed through the evaporator 5 in the 2 nd air passage 23b can be prevented from being increased by mixing the air having passed through the evaporator 5 in the 2 nd air passage 23b with the indoor air taken in from the suction port 21 in the 3 rd air passage 23 b.

The material constituting the 1 st partition 8a and the 2 nd partition 8b may be a material having a lower thermal conductivity than the material constituting the heat transfer tubes and fins through which the refrigerant flows in the evaporator 5 and the 1 st condensation portion 3a. This can reduce the heat exchange between the air in the 1 st air passage 23a, the air in the 2 nd air passage 23b, and the air in the 3 rd air passage 23c by the 1 st partition 8a and the 2 nd partition 8b.

Embodiment 5.

Referring to fig. 11 and 12, a dehumidifying device 1 according to embodiment 5 will be described. The dehumidifier 1 of the present embodiment is different from the dehumidifier 1 of embodiment 4 in that the 2 nd condensation unit 3b and the 3 rd condensation unit 3c are integrated.

In the dehumidifying apparatus 1 of the present embodiment, the 2 nd condensation unit 3b and the 3 rd condensation unit 3c are integrally configured. Specifically, each of the plurality of fins 13 is integrally configured with each of the plurality of fins 17, respectively.

According to the dehumidifying apparatus 1 of the present embodiment, the heat transfer areas of the 2 nd condensation portion 3b and the 3 rd condensation portion 3c are larger than the heat transfer area of the evaporator 5. Further, the 2 nd condensation unit 3b of the 2 nd condensation unit 3b and the 3 rd condensation unit 3c, which are integrally formed, exchange heat with the air passing through the 1 st air passage 23a and the 2 nd air passage 23 b. The 3 rd condensing unit 3c of the 2 nd condensing unit 3b and the 3 rd condensing unit 3c, which are integrally formed, exchanges heat with the air passing through the 3 rd air passage 23c. This can obtain the same effects as those of embodiment 4.

Further, according to the dehumidifying apparatus 1 of the present embodiment, the 2 nd condensation portion 3b and the 3 rd condensation portion 3c are integrally configured. Therefore, the cost of connecting the pipes can be suppressed.

The above embodiments can be appropriately combined.

The embodiments disclosed herein are examples in all respects and should not be considered as limiting. The scope of the present disclosure is shown not by the above description but by the claims, and is intended to include all modifications within the meaning and scope equivalent to the claims.

Description of the reference numerals

1: a dehumidifying device; 2: a compressor; 3: a condenser; 3a: a1 st condensing unit; 3b: a2 nd condensing unit; 3c: a 3 rd condensing unit; 4: a pressure reducing device; 5: an evaporator; 6: a blower; 8a: a1 st partition; 8b: a2 nd partition; 10: a refrigerant circuit; 11. 13, 15, 17: a fin; 12. 14, 16, 18: a heat transfer tube; 20: a housing; 21: a suction inlet; 21a: a1 st suction unit; 21b: a2 nd suction part; 22: a blow-out port; 23: an air path; 23a: a1 st air path; 23b: a2 nd air path; 23c: and 3. A3 rd air path.

Claims (5)

1. A dehumidifying apparatus, wherein the dehumidifying apparatus comprises:

a housing; and

a blower and a refrigerant circuit disposed in the housing,

the blower is configured to send out air,

the refrigerant circuit has a compressor, a condenser, a pressure reducing device, and an evaporator, and is configured to circulate a refrigerant in the order of the compressor, the condenser, the pressure reducing device, and the evaporator,

the condenser includes a1 st condensation part and a2 nd condensation part, and is configured to flow the refrigerant in the order of the 2 nd condensation part and the 1 st condensation part,

the 1 st condensation part is arranged at the leeward side of the evaporator,

the 2 nd condensation part is arranged on the leeward side of the 1 st condensation part,

the height of the 1 st condensation part is lower than the height of the evaporator,

the height of the 2 nd condensing part is higher than that of the 1 st condensing part.

2. The dehumidifying apparatus according to claim 1, wherein,

the housing includes: a suction port for taking in the air; a1 st air passage and a2 nd air passage which communicate with the suction port; a1 st partition portion for dividing the first space into a plurality of partitions,

the 1 st air passage and the 2 nd air passage are partitioned by the 1 st partition portion,

in the 1 st air passage, the evaporator, the 1 st condensation unit, the 2 nd condensation unit, and the blower are arranged from upstream to downstream in the flow of the air,

in the 2 nd air duct, the evaporator, the 2 nd condensing unit, and the blower are disposed from the upstream toward the downstream in the flow of the air.

3. The dehumidifying apparatus according to claim 1, wherein,

the condenser includes a 3 rd condensing portion disposed between the compressor and the 2 nd condensing portion in the refrigerant circuit,

the 3 rd condensing part is arranged above the 2 nd condensing part,

the height of the 3 rd condensing part is higher than that of the evaporator.

4. A dehumidifying apparatus as claimed in claim 3, wherein,

the housing includes: a suction port for taking in the air; a1 st air passage, a2 nd air passage, and a 3 rd air passage, which communicate with the suction port; a1 st partition portion and a2 nd partition portion,

the 1 st air passage and the 2 nd air passage are partitioned by the 1 st partition portion,

the 2 nd air passage and the 3 rd air passage are partitioned by the 2 nd partition portion,

in the 1 st air passage, the evaporator, the 1 st condensation unit, the 2 nd condensation unit, and the blower are arranged from upstream to downstream in the flow of the air,

in the 2 nd air passage, the evaporator, the 2 nd condensing unit, and the blower are arranged from the upstream toward the downstream in the flow of the air,

in the 3 rd air duct, the 3 rd condensation unit and the blower are disposed from the upstream side toward the downstream side in the flow of the air.

5. Dehumidifying apparatus according to claim 3 or 4, wherein,

the 2 nd condensing portion and the 3 rd condensing portion are integrally formed.