CN116802441A - Dehumidifying device - Google Patents

Abstract

The dehumidification device (1) is provided with a housing (20), a blower (6), a refrigerant circuit (101), and a heat pipe (102). The refrigerant circuit (101) has a compressor (2), a condenser (3), a pressure reducing device (4), and an evaporator (5). The heat pipe (102) has an auxiliary condenser (9 a) and an auxiliary evaporator (9 b). The evaporator (5) is disposed downstream of the auxiliary evaporator (9 b). The auxiliary condenser (9 a) is disposed downstream of the evaporator (5). The condenser (3) is disposed downstream of the auxiliary condenser (9 a). The heat transfer tube of the auxiliary condenser (9 a) is a round tube. The heat transfer tube of the condenser (3) includes a flat tube.

Description

Dehumidifying device

Technical Field

The present disclosure relates to a dehumidifying apparatus.

Background

Conventionally, in order to improve the performance of a condenser, a dehumidifier using flat tubes for heat transfer tubes of a condenser has been proposed. For example, international publication No. 2019/077744 (patent document 1) describes a dehumidifier using flat tubes for heat transfer tubes of a condenser.

Prior art literature

Patent literature

Patent document 1: international publication No. 2019/077744

Disclosure of Invention

Problems to be solved by the invention

In the dehumidifying apparatus, dehumidified water is condensed on the surface of the evaporator. The dehumidified water splashes to a condenser disposed downstream of the evaporator. When flat tubes are used as the heat transfer tubes of the condenser as described in the above-mentioned document, the dehumidified water stays on the surfaces of the flat tubes. The dehumidified water retained on the surfaces of the flat tubes is heated by the refrigerant in the flat tubes and evaporated, thereby re-humidifying the air. Thereby, the dehumidifying amount of the dehumidifying apparatus is reduced.

The present disclosure has been made in view of the above problems, and an object thereof is to provide a dehumidifying apparatus capable of improving performance of a condenser and improving a dehumidifying amount.

Means for solving the problems

The dehumidifying device of the present disclosure includes a housing, a blower, a refrigerant circuit, and a heat pipe. The blower, the refrigerant circuit and the heat pipe are disposed in 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 the 1 st refrigerant in the order of the compressor, the condenser, the pressure reducing device, and the evaporator. The heat pipe has an auxiliary condenser and an auxiliary evaporator, and is configured such that the 2 nd refrigerant circulates in the order of the auxiliary condenser and the auxiliary evaporator. The condenser has a 1 st heat transfer pipe, and the 1 st heat transfer pipe is configured to flow a 1 st refrigerant. The auxiliary condenser has a 2 nd heat transfer pipe, which 2 nd heat transfer pipe is provided for the 2 nd refrigerant to flow. The evaporator is disposed downstream of the auxiliary evaporator. The auxiliary condenser is disposed downstream of the evaporator. The condenser is disposed downstream of the auxiliary condenser. The 2 nd heat transfer pipe of the auxiliary condenser is a round pipe. The 1 st heat transfer tube of the condenser includes a flat tube.

Effects of the invention

According to the present disclosure, the evaporator is disposed downstream of the auxiliary evaporator. The 2 nd heat transfer tube of the auxiliary condenser is a round tube, and the 1 st heat transfer tube of the condenser comprises a flat tube. Therefore, the performance of the condenser can be improved, and the amount of dehumidification can be improved.

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 auxiliary evaporator, the auxiliary condenser, and the condenser of the dehumidifying apparatus of embodiment 1.

Fig. 4 is a front view of a condenser of the dehumidifier of embodiment 1.

Fig. 5 is a front view of a modified example of a condenser of the dehumidifier of embodiment 1.

Fig. 6 is a side view of the auxiliary condenser and the auxiliary evaporator of the dehumidifying apparatus of embodiment 1.

Fig. 7 is a cross-sectional view of an evaporator and a condenser of the dehumidifying apparatus of the comparative example of embodiment 1.

Fig. 8 is a refrigerant circuit diagram of the dehumidifying apparatus of embodiment 2.

Fig. 9 is a schematic diagram showing the structure of the dehumidifying device according to embodiment 2.

Fig. 10 is a cross-sectional view of the auxiliary evaporator, the auxiliary condenser, the 1 st condensation unit, the 2 nd condensation unit, and the 3 rd condensation unit of the dehumidifier of embodiment 2.

Fig. 11 is a cross-sectional view of the auxiliary evaporator, the auxiliary condenser, the 1 st condensation unit, the 2 nd condensation unit, and the 3 rd condensation unit of the dehumidifier of embodiment 3.

Fig. 12 is a cross-sectional view of the auxiliary evaporator, the auxiliary condenser, the 1 st condensation unit, the 2 nd condensation unit, and the 3 rd condensation unit of the dehumidifier of embodiment 4.

Fig. 13 is a cross-sectional view of the auxiliary evaporator, the auxiliary condenser, 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 dehumidifying apparatus 1 includes: a refrigerant circuit 101 having a compressor 2, a condenser 3, a pressure reducing device 4, and an evaporator 5; a heat pipe 102 having an auxiliary condenser 9a and an auxiliary evaporator 9b; a blower 6; a drain pan 7; and a housing 20. The refrigerant circuit 101, the heat pipe 102, the blower 6, and the drain pan 7 are disposed in the casing 20. The housing 20 faces an external space (indoor space) to be dehumidified by the dehumidifier 1.

The refrigerant circuit 101 is configured to circulate a refrigerant (refrigerant 1) in the order of the compressor 2, the condenser 3, the pressure reducing device 4, and the evaporator 5. Specifically, the refrigerant circuit 101 is configured by connecting the compressor 2, the condenser 3, the pressure reducing device 4, and the evaporator 5 in this order by pipes. The refrigerant passes through the pipe, and circulates through the refrigerant circuit 101 in the order of the compressor 2, the condenser 3, the pressure reducing device 4, and the evaporator 5. In fig. 2, solid arrows marked in the refrigerant circuit 101 show the flow of the refrigerant in the refrigerant circuit 101. In the present embodiment, the refrigerant (refrigerant 1) in the refrigerant circuit 101 is different from the refrigerant (refrigerant 2) in the heat pipe 102. The refrigerant (refrigerant 1) in the refrigerant circuit 101 may be the same as the refrigerant (refrigerant 2) in the heat pipe 102.

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 condenser 3 is disposed downstream of the auxiliary condenser 9a in the air flow generated by the blower 6. That is, the condenser 3 is disposed downstream of the auxiliary condenser 9 a. The condenser 3 has a heat transfer pipe (1 st heat transfer pipe) through which a refrigerant (1 st refrigerant) flows. The heat transfer pipe (1 st heat transfer pipe) of the condenser 3 includes a flat pipe.

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 downstream of the auxiliary evaporator 9b in the air flow generated by the blower 6. That is, the evaporator 5 is disposed downstream of the auxiliary evaporator 9 b. The heat transfer tube of the evaporator 5 is a circular tube.

The heat pipe 102 is configured such that the refrigerant (refrigerant 2) circulates in the order of the auxiliary condenser 9a and the auxiliary evaporator 9 b. Specifically, the heat pipe 102 is configured by connecting an outlet of the auxiliary condenser 9a to an inlet of the auxiliary evaporator 9b, and an inlet of the auxiliary condenser 9a to an outlet of the auxiliary evaporator 9b, respectively, by pipes. The refrigerant passes through the pipe and circulates through the heat pipe 102 in the order of the auxiliary condenser 9a and the auxiliary evaporator 9 b. In the present embodiment, the heat pipe 102 is configured such that the refrigerant (refrigerant 2) circulates naturally in the order of the auxiliary condenser 9a and the auxiliary evaporator 9 b. In fig. 2, dashed arrows labeled in heat pipe 102 illustrate the flow of refrigerant in heat pipe 102.

The auxiliary condenser 9a is configured to heat the air taken in from the outside of the casing 20 by the blower 6 before the air flows into the condenser 3. The auxiliary condenser 9a is a reheater. The auxiliary condenser 9a is configured to condense and cool the refrigerant. The auxiliary condenser 9a is a heat exchanger that exchanges heat between the refrigerant and the air. The auxiliary condenser 9a has refrigerant inlets and outlets, and air inlets and outlets. The refrigerant inlet of the auxiliary condenser 9a is connected to the outlet of the auxiliary evaporator 9b through a pipe. The auxiliary condenser 9a is disposed downstream of the evaporator 5 in the air flow generated by the blower 6. That is, the auxiliary condenser 9a is disposed downstream of the evaporator 5. The auxiliary condenser 9a has a heat transfer pipe (2 nd heat transfer pipe) through which the refrigerant (2 nd refrigerant) flows. The heat transfer pipe (2 nd heat transfer pipe) of the auxiliary condenser 9a is a round pipe.

The auxiliary evaporator 9b is configured to cool the air taken in from the outside of the casing 20 by the blower 6 in advance before the air flows into the evaporator 5. The auxiliary evaporator 9b is a pre-cooler. The auxiliary evaporator 9b is configured to evaporate the refrigerant and heat the refrigerant. The auxiliary evaporator 9b is a heat exchanger that exchanges heat between the refrigerant and the air. The auxiliary evaporator 9b has refrigerant inlets and outlets, and air inlets and outlets. The refrigerant inlet of the auxiliary evaporator 9b is connected to the outlet of the auxiliary condenser 9a through a pipe. The auxiliary evaporator 9b is disposed upstream of the evaporator 5 in the air flow generated by the blower 6. That is, the auxiliary evaporator 9b is disposed upstream of the evaporator 5. The heat transfer tube of the auxiliary evaporator 9b is a round tube.

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 into the inside and send it out to the condenser 3, the evaporator 5, the auxiliary condenser 9a, and the auxiliary evaporator 9 b. Specifically, the blower 6 is configured to take in air from an external space (indoor space) into the casing 20, pass the air through the auxiliary evaporator 9b, the evaporator 5, the auxiliary condenser 9a, and the condenser 3, and then discharge the air 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 auxiliary evaporator 9B, the evaporator 5, the auxiliary condenser 9a, and the condenser 3 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. 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 auxiliary evaporator 9b, the evaporator 5, the auxiliary condenser 9a, the condenser 3, and the blower 6 are disposed in the air passage 23. Therefore, the auxiliary evaporator 9b, the evaporator 5, the auxiliary condenser 9a, and the condenser 3 are disposed in the same air passage 23. The auxiliary evaporator 9b, the evaporator 5, the auxiliary condenser 9a, and the condenser 3 are disposed in the air passage 23 in the order of the auxiliary evaporator 9b, the evaporator 5, the auxiliary condenser 9a, and the condenser 3 from upstream to downstream in the air flow.

In the air duct 23, air sucked into the casing 20 from the outside of the casing 20 through the suction port 21 passes through the auxiliary evaporator 9b, the evaporator 5, the auxiliary condenser 9a, and the condenser 3 in this order, 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, the blower 6, the auxiliary condenser 9a, and the auxiliary evaporator 9 b. For example, the pressure reducing device 4 may be disposed in the air duct 23.

In addition, when the dehumidifier 1 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 installed on the equipment itself or may be provided on the window side.

The drain pan 7 is configured to drain the drain pan 7 with the dehumidified water condensed on the evaporator 5 or the dehumidified water splashed from the evaporator 5. In the present embodiment, the auxiliary evaporator 9b, the evaporator 5, the auxiliary condenser 9a, and the condenser 3 are disposed on the drain pan 7.

Next, the structures of the auxiliary evaporator 9b, the evaporator 5, the auxiliary condenser 9a, and the condenser 3 will be described in detail with reference to fig. 3 to 5. Fig. 3 is a cross-sectional view of auxiliary evaporator 9b, evaporator 5, auxiliary condenser 9a, and condenser 3 in embodiment 1. In fig. 3, for convenience of explanation, the auxiliary evaporator 9b, the evaporator 5, the auxiliary condenser 9a, and a part of the condenser 3 are illustrated.

In the dehumidifying device 1 of the present embodiment, the condenser 3 has a plurality of fins 11 and heat transfer tubes (1 st heat transfer tube) 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 is configured to have a cross-sectional shape extending in the column direction. The heat transfer tube 12 has a plurality of linear portions that extend linearly in the stacking direction of the plurality of fins 11. The condenser 3 includes a 1 st header 31 and a 2 nd header 32 (see fig. 4) connecting the ends of the plurality of straight portions. The heat transfer pipe 12 has a plurality of small-diameter pipes at a plurality of straight portions. The heat transfer pipe 12 is configured to flow a refrigerant. The heat transfer tube 12 is a flat tube. The heat transfer pipe 12 is a flat pipe having a flat shape with respect to the flow direction of the air passing through the air duct 23. The heat transfer pipe 12 is configured to have a flat shape extending in the direction in which the condenser 3 and the auxiliary condenser 9a are arranged.

The evaporator 5 has a plurality of fins 13 and heat transfer pipes 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 straight 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.

The auxiliary condenser 9a 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 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 16 is configured to flow a refrigerant. The heat transfer pipe 16 is a circular pipe.

The auxiliary evaporator 9b has a plurality of fins 17 and heat transfer tubes 18. The plurality of fins 17 are each formed in a thin plate shape. The plurality of fins 17 are arranged to be stacked on each other. The heat transfer pipe 18 is configured as a plurality of fins 17 stacked through each other in the stacking direction. The heat transfer pipe 18 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 18 is configured 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 18 is configured to flow a refrigerant. The heat transfer pipe 18 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 condenser 3, the plurality of fins 13 of the evaporator 5, the plurality of fins 15 of the auxiliary condenser 9a, and the plurality of fins 17 of the auxiliary evaporator 9b, respectively. In the condenser 3, in the cross section shown in fig. 3, straight portions among the plurality of heat transfer pipes 12 are arranged. The shape of the straight portions of the plurality of heat transfer pipes 12 may be the same as each other.

In the present embodiment, the straight portions of the plurality of heat transfer tubes 12 are arranged in the segment direction to be 3 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. That is, the centers of the straight portions in the plurality of heat transfer tubes 12 arranged in the segment direction are arranged in a straight line. Further, the intervals between the straight portions in the heat transfer tubes 12 of the respective stages may be the same as each other.

Fig. 4 is a front view of the condenser 3 when the condenser 3 is viewed from the column direction. The flat tubes of the condenser 3 may be arranged in the horizontal direction or in the vertical direction. The fins 11 of the condenser 3 may be plate fins, corrugated fins, or the like. The shape of the fins 11 of the condenser 3 is selected according to the performance of the condenser 3 and the installation posture of the flat tubes of the condenser 3. The heat transfer tube 12 of the condenser 3 includes at least one refrigerant path. In the present embodiment, the number of refrigerant paths gradually decreases from upstream to downstream of the flow of the refrigerant.

Referring to fig. 2 and 4, the 1 st header 31 has a refrigerant inlet and a refrigerant outlet. In the present embodiment, the refrigerant inlet of the 1 st header 31 is connected to the discharge port of the compressor 2 through a pipe. The refrigerant outlet of the 1 st header 31 is connected to the inlet of the pressure reducing device 4 by piping. By providing the partition 33 in the 1 st header 31 and the 2 nd header 32, the refrigerant flowing in from the compressor 2 is folded back between the 1 st header 31 and the 2 nd header 32 a plurality of times by a plurality of straight portions, and then flows out from the refrigerant outlet of the 1 st header 31 to the pressure reducing device 4. In this case, the number of refrigerant paths in the straight line portion that reciprocates between the 1 st header 31 and the 2 nd header 32 preferably gradually decreases from the upstream side to the downstream side of the condenser 3. For example, if the number of refrigerant paths going from the 1 st header 31 to the 2 nd header 32 is 5, the number of refrigerant paths going from the 2 nd header 32 to the 1 st header 31 is preferably 4 or less.

Further, as shown in fig. 5, the 1 st header 31 and the 2 nd header 32 may also be divided. Thus, the refrigerant flowing in from the compressor 2 may be returned between the 1 st header 31 and the 2 nd header 32 a plurality of times by the plurality of straight portions, and then may flow out from the refrigerant outlet of the condenser 3 to the pressure reducing device 4. The 1 st header 31 includes a 1 st header upstream portion 311 and a 1 st header downstream portion 312 that are divided from each other. The 2 nd header 32 includes a 2 nd header upstream portion 321 and a 2 nd header downstream portion 322 that are divided from each other. The refrigerant outlet of the condenser 3 may be located not in the 1 st header 31 but in the 2 nd header 32. In this case, the pipe connecting the pressure reducing device 4 and the condenser 3 and the pipe connecting the compressor 2 and the condenser 3 are located on the opposite side with the condenser 3 interposed therebetween.

In the evaporator 5, in the cross section shown in fig. 3, straight portions among the plurality of heat transfer tubes 14 are arranged. The outer diameter and the inner diameter of the straight portions in these plurality of heat transfer pipes 14 may be the same as each other.

In the present embodiment, the straight portions of the plurality of heat transfer tubes 14 are arranged in 3 columns in the column direction. The intervals between the straight portions in the heat transfer tubes 14 arranged in each of the 3 rows in the row direction may be the same as each other. The interval is a distance between centers of straight portions in the heat transfer tubes 14 arranged in each row adjacent to each other in the row direction. In the present embodiment, the straight portions in 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 in the plurality of heat transfer tubes 14 of the respective columns 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 in 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 in the plurality of heat transfer tubes 14 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 straight portions of the plurality of heat transfer tubes 14 are arranged in each 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 in 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 in the plurality of heat transfer tubes 14 arranged in each of the columns at both ends in the column direction of the 3 columns are the same as each other. Further, the positions in the segment direction of the straight portions in the heat transfer tubes 14 in the column arranged at the center in the column direction of these 3 columns are arranged at the center between the positions in the segment direction of the straight portions in the plurality of heat transfer tubes 14 in each of the columns arranged at both ends.

In the auxiliary condenser 9a, in the cross section shown in fig. 3, straight portions among the plurality of heat transfer pipes 16 are arranged. The outer diameter and the inner diameter of the straight portions in these plurality of heat transfer tubes 16 may be the same as each other.

In the present embodiment, the straight portions of the plurality of heat transfer tubes 16 are arranged in 1 row in the row direction, but may be arranged in a plurality of rows. In this case, the arrangement and the distance in the column direction of the straight portions in the plurality of heat transfer pipes 16 are based on the arrangement and the distance in the column direction of the straight portions in the plurality of heat transfer pipes 14.

In the present embodiment, the straight portions of the plurality of heat transfer tubes 16 are arranged in each 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 in the plurality of heat transfer tubes 16 arranged in the segment direction in each column are arranged in a straight line. Further, the intervals between the straight portions in the heat transfer tubes 16 of the respective stages may be the same as each other.

In the auxiliary evaporator 9b, in the cross section shown in fig. 3, straight portions among the plurality of heat transfer tubes 18 are arranged. The outer diameter and the inner diameter of the straight portions in these plurality of heat transfer tubes 18 may be the same as each other.

In the present embodiment, the linear portions of the plurality of heat transfer tubes 18 are arranged in 1 row in the row direction, but may be arranged in a plurality of rows. In this case, the arrangement and the distance in the column direction of the straight portions in the plurality of heat transfer tubes 18 are based on the arrangement and the distance in the column direction of the straight portions in the plurality of heat transfer tubes 18.

In the present embodiment, the straight portions of the plurality of heat transfer tubes 18 are arranged in each 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 18 are arranged in a linear manner in the segment direction in each row. That is, the centers of the straight portions in the plurality of heat transfer tubes 18 arranged in the segment direction in each column are arranged in a straight line. The intervals between the straight portions in the heat transfer tubes 18 of the respective stages may be the same as each other.

Referring to fig. 6, in the present embodiment, the refrigerant inlet of the auxiliary condenser 9a is arranged higher than the refrigerant outlet of the auxiliary evaporator 9b in the column direction, and the refrigerant outlet of the auxiliary condenser 9a is arranged higher than the refrigerant inlet of the auxiliary evaporator 9 b. The solid arrows in fig. 6 show the flow of the refrigerant circulating in the auxiliary condenser 9a and the auxiliary evaporator 9 b.

The evaporator, the auxiliary condenser 9a, and the auxiliary evaporator 9b may be a multi-path heat exchanger having a plurality of refrigerant paths.

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 condenser 3 disposed in the air passage 23. The superheated gas refrigerant flowing into the condenser 3 exchanges heat with air flowing from the outside space into the air passage 23 through the suction port 21 and passing through the auxiliary evaporator 9b, the evaporator 5, and the auxiliary condenser 9a disposed in the air passage 23, and is cooled to a supercooled liquid refrigerant.

On the other hand, the air passing through the condenser 3 disposed in the air duct 23 passes through the auxiliary evaporator 9b, the evaporator 5, and the auxiliary condenser 9a disposed in the air duct 23 as well, and then is heat-exchanged with the superheated gas-state refrigerant or the gas-liquid two-phase-state refrigerant in the condenser 3 to be heated.

The supercooled liquid refrigerant flowing out of the condenser 3 is decompressed by the decompressing device 4 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 passing through the auxiliary evaporator 9b disposed in the air passage 23, 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 passes through the auxiliary evaporator 9b disposed in the air passage 23, and then exchanges heat with the refrigerant in the gas-liquid two-phase state in the evaporator 5, and is cooled to a temperature equal to or lower than the dew point of the air, thereby being dehumidified.

The refrigerant in a gas-liquid two-phase state or a gas state, which is sealed in the auxiliary condenser 9a, is cooled by heat exchange with air passing through the auxiliary evaporator 9b and the evaporator 5 disposed in the air passage 23, and becomes a supercooled liquid state refrigerant. Since the density of the liquid refrigerant is higher than that of the gas refrigerant, the supercooled liquid refrigerant is lowered in the auxiliary condenser 9 a. Since the outlet pipe of the auxiliary condenser 9a is arranged higher than the inlet pipe of the auxiliary evaporator 9b, the refrigerant in the supercooled liquid state flows into the auxiliary evaporator 9b through the pipe.

On the other hand, the air passing through the auxiliary condenser 9a disposed in the air duct 23 passes through the auxiliary evaporator 9b and the evaporator 5 also disposed in the 1 st air duct 23a, and then undergoes heat exchange with the refrigerant in the gas-liquid two-phase state or the gas state in the auxiliary condenser 9a, thereby being heated.

The supercooled liquid refrigerant flowing into the auxiliary evaporator 9b is heated by heat exchange with the air taken into the air passage 23 from the suction port 21, and is a gas-liquid two-phase refrigerant or a superheated gas refrigerant. The gas refrigerant has a density smaller than that of the liquid refrigerant, and thus rises in the auxiliary evaporator 9 b. Since the inlet pipe of the auxiliary condenser 9a is arranged higher than the outlet pipe of the auxiliary evaporator 9b, the gas refrigerant flows into the auxiliary condenser 9a through the pipe. In this way, the refrigerant circulates naturally in the auxiliary condenser 9a and the auxiliary evaporator 9 b.

On the other hand, the air passing through the auxiliary evaporator 9b disposed in the air passage 23 is taken into the air passage 23 through the suction port 21, and then is cooled by heat exchange with the refrigerant in the gas-liquid two-phase state or the liquid state in the auxiliary evaporator 9 b.

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

Fig. 7 is a sectional view of the evaporator 5 and the condenser 3 of the dehumidifying apparatus 1 of the comparative example. In order to improve the performance of the condenser 3, the heat transfer tube 12 of the condenser 3 is a flat tube having heat transfer performance superior to that of a round tube. However, in general, in a dehumidifier in which the condenser 3 is disposed on the downstream side of the evaporator 5, dehumidified water splashes onto the condenser 3. In the condenser 3, in which the heat transfer tube 12 is a flat tube having a flat shape, dehumidified water stays on the surface of the flat tube, is heated by the refrigerant, and evaporates, thereby re-humidifying the air. Thereby, the dehumidifying amount of the dehumidifying apparatus 1 is reduced. Therefore, in the dehumidifying apparatus 1 of the comparative example, the dehumidifying amount cannot be increased while improving the performance of the condenser 3.

According to the dehumidifying apparatus 1 of the present embodiment, the heat transfer tube 16 of the auxiliary condenser 9a is a circular tube. The auxiliary condenser 9a is disposed between the evaporator 5 and the condenser 3. Therefore, the dehumidified water splashed from the evaporator 5 to the auxiliary condenser 9a can be suppressed from being retained in the heat transfer pipe 16. This can improve the drainage of the auxiliary condenser 9 a. Therefore, the dehumidification water retained in the heat transfer tube 16 of the auxiliary condenser 9a can be suppressed from being heated by the refrigerant and evaporated, and the air can be re-humidified. This can increase the dehumidifying amount of the dehumidifying apparatus 1. Further, the heat transfer tube 12 of the condenser 3 includes a flat tube. The heat transfer performance of the flat tube is superior to that of the round tube. This can improve the performance of the condenser 3. The evaporator 5 is disposed downstream of the auxiliary evaporator 9 b. Therefore, in the heat pipe 102, the auxiliary evaporator 9b cools the air taken in from the intake port 21, and thereby the relative humidity of the air passing through the evaporator 5 can be increased. By increasing the relative humidity of the air passing through the evaporator 5, the amount of dehumidification in the evaporator 5 can be increased. Therefore, the performance of the condenser 3 can be improved, and the amount of dehumidification can be improved.

Further, since the auxiliary condenser 9a has the plate fins and the round tube heat transfer tubes, it is possible to suppress the splash of the dehumidified water to the condenser 3 having the flat tube heat transfer tubes. Further, the auxiliary condenser 9a, which combines the plate fins and the round tube, discharges the dehumidified water to the drain pan 7 along the plate fins from both sides in the radial direction of the round tube, and therefore, the drainage performance is superior to that of the flat tube. Therefore, it is possible to suppress a decrease in heat exchange performance due to retention of the dehumidified water and a decrease in the amount of dehumidification due to heating of the dehumidified water.

In the heat pipe 102, the auxiliary condenser 9a increases the temperature of the air passing through the condenser 3 disposed in the air passage 23, and thus increases the condensation temperature of the refrigerant in the condenser 3. Thereby, the difference between the condensing pressure and the evaporating pressure in the refrigerant circuit increases, and thus the input in the compressor 2 increases. However, by combining the auxiliary condenser 9a and the condenser 3 in which the heat transfer tube 12 is a flat tube having a higher heat transfer performance than a round tube, the rise in condensing temperature can be reduced, and the difference between the condensing pressure and the evaporating pressure in the refrigerant circuit can be reduced. Thus, an increase in input in the compressor 2 can be reduced.

Further, according to the dehumidifying apparatus 1 of the present embodiment, in the condenser 3, the number of refrigerant paths gradually decreases from upstream to downstream of the flow of the refrigerant. That is, in the condenser 3, the number of refrigerant paths in the 1 st straight line portion that reciprocates between the 1 st header 31 and the 2 nd header 32 gradually decreases from the upstream side to the downstream side. Since the pressure loss of the refrigerant in the gas state on the upstream side is larger than the pressure loss of the refrigerant in the gas-liquid two-phase state, the number of refrigerant paths is increased for the refrigerant in the gas state on the upstream side to thereby reduce the flow velocity, and the pressure loss can be reduced. Further, since the pressure loss of the refrigerant in the gas-liquid two-phase state on the downstream side is smaller than the pressure loss of the refrigerant in the gas state, the flow rate of the refrigerant in the gas-liquid two-phase state on the downstream side is increased by reducing the number of refrigerant paths, whereby the heat transfer rate can be improved.

Embodiment 2.

Referring to fig. 8 to 10, 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 a 1 st condensation unit 3a, a 2 nd condensation unit 3b, a 3 rd condensation unit 3c, a 1 st suction inlet 21a, a 2 nd suction inlet 21b, a partition 8, a 1 st air passage 23a, and a 2 nd air passage 23 b.

Referring to fig. 8 and 9, in the dehumidifying apparatus 1 of the present embodiment, the housing 20 has a 1 st suction port 21a, a 2 nd suction port 21b, a 1 st air path 23a, and a 2 nd air path 23b. The 1 st suction port 21a is used for taking in air. The 1 st air passage 23a communicates with the 1 st suction port 21 a. The 2 nd suction port 21b is used for taking in air. The 2 nd air path 23b communicates with the 2 nd suction port 21 b. The 2 nd air path 23b is separated from the 1 st air path 23 a.

The condenser 3 includes a 1 st condensation portion 3a, a 2 nd condensation portion 3b, and a 3 rd condensation portion 3c. The condenser 3 is configured such that the refrigerant (1 st refrigerant) flows in the order of the 3 rd condensation unit 3c, the 2 nd condensation unit 3b, and the 1 st condensation unit 3 a. The 1 st condensation unit 3a is connected to the 2 nd condensation unit 3b. The 2 nd condensation unit 3b is connected to the 3 rd condensation unit 3c. The refrigerant circuit 101 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 heat transfer pipe 12 of the condenser 3 includes a heat transfer pipe 12a of the 1 st condensation portion 3a, a heat transfer pipe 12b of the 2 nd condensation portion 3b, and a heat transfer pipe 12c of the 3 rd condensation portion 3c.

Referring to fig. 9 and 10, 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 11c and heat transfer tubes 12c. The 3 rd condensing portion 3c has a refrigerant inlet and outlet, and an air inlet and outlet. In the present embodiment, 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. The heat transfer tube 12c is a flat tube.

The 2 nd condensing unit 3b is configured to further condense and cool the refrigerant cooled by the 3 rd condensing unit 3 c. 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 plurality of fins 11b and heat transfer tubes 12b. 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 and outlet of the 2 nd condensation unit 3b are connected to the outlet of the 3 rd condensation unit 3c and the inlet of the 1 st condensation unit 3a, respectively, by piping. 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 3 a. The heat transfer tube 12b of the 2 nd condensation unit 3b is a flat tube.

The 1 st condensation unit 3a is configured to further condense and cool the refrigerant cooled by the 2 nd condensation unit 3 b. The 1 st condensation unit 3a is a heat exchanger that exchanges heat between the refrigerant and air. The 1 st condensation unit 3a has a plurality of fins 11a and heat transfer tubes 12a. 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 and outlet of the 1 st condensation unit 3a are connected to the outlet of the 2 nd condensation unit 3b and the inlet of the pressure reducing device 4 through pipes, respectively. 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 3 b. The 1 st condensation unit 3a is disposed downstream of the auxiliary condenser 9a in the air flow generated by the blower 6. That is, the 1 st condensation unit 3a is disposed downstream of the auxiliary condenser 9 a. The heat transfer tube 12a of the 1 st condensation unit 3a is a flat tube.

In the present embodiment, the 3 rd condensation unit 3c, the 2 nd condensation unit 3b, and the 1 st condensation unit 3a are flat tube heat exchangers having fins and heat transfer tubes of the same shape. The 3 rd condensation section 3c is located above the 2 nd condensation section 3b in the section direction. That is, the straight portions of the heat transfer tubes 12c in the 3 rd condensation portion 3c and the heat transfer tubes 12b in the 2 nd condensation portion 3b are arranged in a straight line in the segment direction. The heat transfer tubes 12a, 12b, and 12c are not limited to flat tubes, and at least one of the heat transfer tubes 12a and 12b may be a flat tube.

The 1 st suction port 21a and the 2 nd suction port 21b are provided for allowing air to enter the interior of the casing 20 from the outside space (indoor space). The 1 st air passage 23a connects the 1 st suction port 21a and the blowout port 22. The 1 st air passage 23a is provided with an auxiliary evaporator 9b, an evaporator 5, an auxiliary condenser 9a, a 1 st condensation unit 3a, a 2 nd condensation unit 3b, and a blower 6. The auxiliary evaporator 9b, the evaporator 5, the auxiliary condenser 9a, 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 1 st suction port 21a flows in the order of the auxiliary evaporator 9b, the evaporator 5, the auxiliary condenser 9a, the 1 st condensation unit 3a, and the 2 nd condensation unit 3 b. The 2 nd air passage 23b connects the 2 nd suction port 21b and the blowout port 22. The 3 rd condensation unit 3c and the blower 6 are disposed in the 2 nd air passage 23 b. The 3 rd condensing unit 3c is disposed in the 2 nd air duct 23b so that the air taken in from the 2 nd suction port 21b flows through the 3 rd condensing unit 3 c.

In the present embodiment, by rotating the fan 6B about the shaft 6a, the air taken in from the outside space (indoor space) as indicated by the arrow a in the figure passes through the auxiliary evaporator 9B, the evaporator 5, the auxiliary condenser 9a, the 1 st condensation unit 3a, and the 2 nd condensation unit 3B in the 1 st air path 23a as indicated by the arrow B in the figure. By rotating the fan 6B about the shaft 6a, the air taken in from the outside space (indoor space) as indicated by an arrow a 'in the figure passes through the 3 rd condensation unit 3c as indicated by an arrow B' in the figure in the 2 nd air duct 23B. The air passing through the 1 st air passage 23a and the air passing through the 2 nd air passage 23b are mixed with each other and discharged to the outside space (indoor space) of the casing 20 through the outlet 22.

The 1 st air passage 23a and the 2 nd air passage 23b may be separated. The 1 st air passage 23a and the 2 nd air passage 23b may be separated by a partition 8, for example. The 1 st air passage 23a and the 2 nd air passage 23b are formed by, for example, the casing 20 and the partition 8, respectively. In the flow direction of the air in the 2 nd air passage 23b, one end of the partition 8 located on the upstream side is formed at least on the upstream side of the air outlet of the auxiliary evaporator 9 b. In the flow direction, the other end of the partition 8 on the downstream side is formed at a position at least on the downstream side of the air inlet of the 1 st condensation unit 3 a. The partition 8 is formed in a flat plate shape, for example. The partition 8 is fixed to the inside of the housing 20.

According to the dehumidifier 1 of the present embodiment, the auxiliary evaporator 9b, the evaporator 5, the auxiliary condenser 9a, 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 1 st suction port 21a flows in the order of the auxiliary evaporator 9b, the evaporator 5, the auxiliary condenser 9a, the 1 st condensation unit 3a, and the 2 nd condensation unit 3 b. The 3 rd condensing unit 3c is disposed in the 2 nd air duct 23b so that the air taken in from the 2 nd suction port 21b flows through the 3 rd condensing unit 3 c. 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 (L/kWh) indicating the dehumidification amount L per 1kWh, which is an index indicating the dehumidification performance of the dehumidification device 1.

The material constituting the partition 8 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 auxiliary evaporator 9b, the evaporator 5, the auxiliary condenser 9a, and the 1 st condensation portion 3 a. 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 partition 8.

Embodiment 3.

Referring to fig. 11, a dehumidifying apparatus 1 according to embodiment 3 will be described. The dehumidifier 1 of the present embodiment is different from the dehumidifier 1 of embodiment 2 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 11b is integrally configured with each of the plurality of fins 11c, 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 1 st condensation portion 3 a. 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 23 a. The 3 rd condensation unit 3c of the 2 nd condensation unit 3b and the 3 rd condensation unit 3c, which are integrally formed, exchanges heat with the air passing through the 2 nd air passage 23 b. This can obtain the same effects as those of embodiment 2.

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 the header pipe and the connection piping can be suppressed.

Embodiment 4.

Referring to fig. 12, a dehumidifying apparatus 1 according to embodiment 4 will be described. The dehumidifier 1 of the present embodiment is different from the dehumidifier 1 of embodiment 2 in that the heat transfer pipe 12b of the 2 nd condensation unit 3b and the heat transfer pipe 12c of the 3 rd condensation unit 3c are circular pipes.

In the dehumidifier 1 of the present embodiment, the heat transfer pipe (1 st heat transfer pipe) 12a of the 1 st condensation unit 3a is a flat pipe. The heat transfer pipes (1 st heat transfer pipe) of the 2 nd condensation portion 3b and the 3 rd condensation portion 3c are round pipes. That is, the heat transfer pipe 12b of the 2 nd condensation unit 3b and the heat transfer pipe 12c of the 3 rd condensation unit 3c are circular pipes.

According to the dehumidifying apparatus 1 of the present embodiment, the heat transfer pipe 12b of the 2 nd condensation portion 3b and the heat transfer pipe 12c of the 3 rd condensation portion 3c are circular pipes. Since the flat tube has a small diameter, the pressure loss is larger than that of the round tube. In addition, the pressure loss of the refrigerant in the gas state is larger than that of the refrigerant in the liquid state. Therefore, by forming the heat transfer pipe 12b of the 2 nd condensation unit 3b and the heat transfer pipe 12c of the 3 rd condensation unit 3c as circular pipes with small pressure loss, the pressure loss due to the superheated gas can be reduced.

Embodiment 5.

Referring to fig. 13, a dehumidifying apparatus 1 according to embodiment 5 will be described. The dehumidifier 1 of the present embodiment is different from the dehumidifier 1 of embodiment 2 in that the heat transfer pipe 12a of the 1 st condensation unit 3a is a circular pipe.

In the dehumidifier 1 of the present embodiment, the heat transfer pipe (1 st heat transfer pipe) 12a of the 1 st condensation unit 3a is a circular pipe. The heat transfer tubes (1 st heat transfer tube) of the 2 nd condensation portion 3b and the 3 rd condensation portion 3c are flat tubes. That is, the heat transfer tubes 12b of the 2 nd condensation unit 3b and the heat transfer tubes 12c of the 3 rd condensation unit 3c are flat tubes.

According to the dehumidifying apparatus 1 of the present embodiment, the heat transfer pipe 12a of the 1 st condensation portion 3a is a circular pipe. Accordingly, when the auxiliary condenser 9a fails to completely suppress the adhesion of splashed dehumidification water to the 1 st condensation unit 3a, the reduction of the heat exchange performance due to the retention of the dehumidification water and the reduction of the dehumidification amount due to the heating of the dehumidification water can be suppressed. Further, the splashing of the dehumidified water to the 2 nd condensation portion 3b of the heat transfer tube 12b having the flat tubes can be further 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 scope of the claims, and is intended to include all modifications within the meaning and scope equivalent to the scope of the claims.

Description of the reference numerals

1: a dehumidifying device; 2: a compressor; 3: a condenser; 3a: a 1 st condensing unit; 3b: a 2 nd condensing unit; 3c: a 3 rd condensing unit; 4: a pressure reducing device; 5: an evaporator; 6: a blower; 7: a drain pan; 8: a partition portion; 9a: an auxiliary condenser; 9b: an auxiliary evaporator; 11. 11a, 11b, 11c, 13, 15, 17: a fin; 12. 12a, 12b, 12c, 14, 16, 18: a heat transfer tube; 20: a housing; 21: a suction inlet; 21a: a 1 st suction inlet; 21b: a 2 nd suction inlet; 22: a blow-out port; 23: an air path; 23a: a 1 st air path; 23b: a 2 nd air path; 31: a 1 st header; 32: a 2 nd header; 33: a partition; 101: a refrigerant circuit; 102: a heat pipe.

Claims (6)

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

a housing; and

a blower, a refrigerant circuit, and a heat pipe, which are 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 1 st refrigerant in the order of the compressor, the condenser, the pressure reducing device, and the evaporator,

the heat pipe has an auxiliary condenser and an auxiliary evaporator, and is configured such that the 2 nd refrigerant circulates in the order of the auxiliary condenser and the auxiliary evaporator,

the condenser has a 1 st heat transfer pipe, the 1 st heat transfer pipe being for the 1 st refrigerant to flow,

the auxiliary condenser has a 2 nd heat transfer pipe, the 2 nd heat transfer pipe being for the 2 nd refrigerant to flow,

the evaporator is arranged on the leeward side of the auxiliary evaporator,

the auxiliary condenser is disposed downstream of the evaporator,

the condenser is disposed downstream of the auxiliary condenser,

the 2 nd heat transfer pipe of the auxiliary condenser is a circular pipe,

the 1 st heat transfer tube of the condenser comprises a flat tube.

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

the 1 st heat transfer tube of the condenser comprises at least one refrigerant path,

the number of the refrigerant paths gradually decreases from upstream to downstream of the flow of the 1 st refrigerant.

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

the housing has: a 1 st suction port for taking in the air; a 1 st air passage communicating with the 1 st suction port; a 2 nd suction port for taking in the air; and a 2 nd air passage communicating with the 2 nd suction port and spaced apart from the 1 st air passage,

the condenser has a 1 st condensation part, a 2 nd condensation part and a 3 rd condensation part, and is configured such that the 1 st refrigerant flows in the order of the 3 rd condensation part, the 2 nd condensation part and the 1 st condensation part,

the auxiliary evaporator, the auxiliary condenser, the 1 st condensing unit, and the 2 nd condensing unit are disposed in the 1 st air passage so that the air taken in from the 1 st suction port flows in the order of the auxiliary evaporator, the auxiliary condenser, the 1 st condensing unit, and the 2 nd condensing unit,

The 3 rd condensation unit is disposed in the 2 nd air passage so that the air taken in from the 2 nd suction port flows through the 3 rd condensation unit.

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

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

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

the 1 st heat transfer pipe of the 1 st condensation portion is a flat pipe,

the 2 nd condensation part and the 1 st heat transfer pipe of the 3 rd condensation part are round pipes.

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

the 1 st heat transfer pipe of the 1 st condensation part is a circular pipe,

the 1 st heat transfer tubes of the 2 nd condensation portion and the 3 rd condensation portion are flat tubes.