Dehumidification device

Abstract

This dehumidifying device comprises a casing, a blower, and a refrigerant circuit. The blower and the refrigerant circuit are disposed inside the casing. The blower is configured so as to blow air. The refrigerant circuit has a compressor, a condenser (3), a decompression device, and an evaporator (5), and the refrigerant circuit is configured so as to circulate refrigerant sequentially through the compressor, the condenser (3), the decompression device, and the evaporator (5). The condenser (3) has a first heat transfer tube (12) through which the refrigerant flows. The evaporator (5) has a second heat transfer tube (14) through which the refrigerant flows. The condenser (3) is disposed downstream of the evaporator (5). The first heat transfer tube (12) of the condenser (3) is a flat tube and extends horizontally. The second heat transfer tube (14) of the evaporator (5) is a flat tube and extends vertically.

Description

Technical Field

[0001] The present disclosure relates to a dehumidifying device.

Background Art

[0002] Conventionally, in order to improve the performance of a heat exchanger, a dehumidifying device using flat tubes for heat transfer tubes has been proposed. For example, International Publication No. 2019 / 077744 (Patent Document 1) describes a dehumidifying device using flat tubes for the heat transfer tubes of a condenser. In the dehumidifying device described in this document, circular tubes are used for the heat transfer tubes of the evaporator.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] In the above document, since circular tubes are used for the heat transfer tubes of the evaporator, it is difficult to improve the performance of the evaporator.

[0005] In a dehumidifying device, dehumidified water condenses on the surface of the evaporator. When the flat tubes described in the above document are used for the heat transfer tubes of the evaporator, since the drainage property of the flat tubes is poor, dehumidified water stays on the surface of the flat tubes of the evaporator. The dehumidified water staying on the surface of the flat tubes of the evaporator inhibits the heat exchange between the refrigerant and air inside the flat tubes, so the heat transfer performance of the evaporator decreases. As a result, the dehumidification amount of the dehumidifying device decreases.

[0006] The present disclosure has been made in view of the above problems, and an object thereof is to provide a dehumidifying device capable of improving the performance of an evaporator and improving the dehumidification amount.

Means for Solving the Problems

[0007] The dehumidifying device according to the present disclosure includes a housing, a blower, and a refrigerant circuit. The blower and the refrigerant circuit are arranged inside the housing. The blower is configured to blow air. The refrigerant circuit has a compressor, a condenser, a decompression device, and an evaporator, and is configured to circulate refrigerant in the order of the compressor, the condenser, the decompression device, and the evaporator. The condenser has a first heat transfer tube through which the refrigerant flows. The evaporator has a second heat transfer tube through which the refrigerant flows. The condenser is arranged downstream of the evaporator in the direction of the wind. The first heat transfer tube of the condenser is a flat tube and extends in the horizontal direction. The second heat transfer tube of the evaporator is a flat tube and extends in the vertical direction. The cross-sectional shape of the first heat transfer tube is configured to have a flat shape extending in the direction in which the condenser and the evaporator are arranged. The cross-sectional shape of the second heat transfer tube is configured to have a flat shape extending in the direction in which the condenser and the evaporator are arranged.

Advantages of the Invention

[0008] According to the dehumidifying device of the present disclosure, the second heat transfer tube of the evaporator is a flat tube and extends in the vertical direction. Therefore, the performance of the evaporator can be improved, and the dehumidification amount can be improved.

Brief Description of the Drawings

[0009]

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Embodiments for Carrying Out the Invention

[0010] Hereinafter, embodiments will be described with reference to the drawings. In the drawings, the same or corresponding parts are denoted by the same reference numerals and their descriptions are not repeated.

[0011] Embodiment 1. With reference to FIGS. 1 and 2, the configuration of the dehumidifying device 1 according to Embodiment 1 will be described. FIG. 1 is a refrigerant circuit diagram of the dehumidifying device 1 according to Embodiment 1. FIG. 2 is a schematic diagram showing the configuration of the dehumidifying device 1 according to Embodiment 1.

[0012] As shown in FIGS. 1 and 2, the dehumidifying device 1 includes a refrigerant circuit 101 having a compressor 2, a condenser 3, a decompression device 4, and an evaporator 5, a blower 6, a drain pan 7, and a housing 20. The refrigerant circuit 101, the blower 6, and the drain pan 7 are disposed inside the housing 20. The housing 20 faces an external space (indoor space) to be dehumidified by the dehumidifying device 1.

[0013] The refrigerant circuit 101 is configured to circulate the refrigerant in the order of the compressor 2, the condenser 3, the decompression device 4, and the evaporator 5. Specifically, the refrigerant circuit 101 is configured by connecting the compressor 2, the condenser 3, the decompression device 4, and the evaporator 5 in this order by piping. Then, the refrigerant circulates through this piping in the order of the compressor 2, the condenser 3, the decompression device 4, and the evaporator 5 in the refrigerant circuit 101. In FIG. 2, the solid line arrows attached to the refrigerant circuit 101 indicate the flow of the refrigerant in the refrigerant circuit 101.

[0014] The compressor 2 is configured to compress the refrigerant. Specifically, the compressor 2 is configured to suck in low-pressure refrigerant from the suction port and compress it, and discharge it as high-pressure refrigerant from the discharge port. The compressor 2 may be configured such that the discharge capacity of the refrigerant is variable. Specifically, the compressor 2 may be an inverter compressor. When the compressor 2 is configured such that the discharge capacity of the refrigerant is variable, the refrigerant circulation amount in the dehumidifying device 1 can be controlled by adjusting the discharge capacity of the compressor 2.

[0015] The condenser 3 is configured to condense and cool the refrigerant pressurized by the compressor 2. The condenser 3 is a heat exchanger that performs heat exchange between the refrigerant and air. The condenser 3 has an inlet and an outlet for the refrigerant, and an inlet and an outlet for air. The refrigerant inlet of the condenser 3 is connected by piping to the discharge port of the compressor 2. The condenser 3 is arranged downstream of the evaporator 5 in the air flow generated by the blower 6. That is, the condenser 3 is arranged downstream of the evaporator 5 with respect to the wind direction. The heat transfer tubes of the condenser 3 are flat tubes.

[0016] The decompression device 4 is configured to decompress and expand the refrigerant cooled by the condenser 3. The decompression device 4 is, for example, an expansion valve. This expansion valve may be an electronically controlled valve. Note that the decompression device 4 is not limited to an expansion valve and may be a capillary tube. The decompression device 4 is connected by piping to each of the refrigerant outlet of the condenser 3 and the refrigerant inlet of the evaporator 5.

[0017] 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 performs heat exchange between the refrigerant and air. The evaporator 5 has an inlet and an outlet for the refrigerant, and an inlet and an outlet for air. The refrigerant outlet of the evaporator 5 is connected by piping to the suction port of the compressor 2. The evaporator 5 is arranged upstream of the condenser 3 in the air flow generated by the blower 6. That is, the evaporator 5 is arranged upstream of the condenser 3 with respect to the wind direction. The heat transfer tubes of the evaporator 5 are flat tubes.

[0018] The blower 6 is configured to blow air. The blower 6 is configured to take in air from the outside of the housing 20 into the housing 20 and blow the air to the condenser 3 and the evaporator 5. Specifically, the blower 6 is configured to take in air from the external space (indoor space) into the housing 20, pass the air through the evaporator 5 and the condenser 3, and then discharge the air outside the housing 20.

[0019] In this embodiment, the blower 6 has a shaft 6a and a fan 6b that rotates about the shaft 6a. As the fan 6b rotates about the shaft 6a, the air taken in from the external space (indoor space) as indicated by the arrow A in the figure passes through the evaporator 5 and the condenser 3 in sequence as indicated by the arrow B in the figure, and is then discharged again into the external space (indoor space) as indicated by the arrow C in the figure. In this way, the air circulates through the external space (indoor space) via the dehumidifying device 1.

[0020] The housing 20 is provided with a suction port 21 for introducing air from the external space (indoor space) to be dehumidified into the interior of the housing 20, and a blowout port 22 for blowing air from the interior of the housing 20 into the external space (indoor space). The housing 20 also has an air passage (air flow path) 23 that connects the suction port 21 and the blowout port 22. The evaporator 5, the condenser 3, and the blower 6 are arranged in the air passage 23. Therefore, the evaporator 5 and the condenser 3 are arranged in the same air passage 23. The evaporator 5 and the condenser 3 are arranged in the air passage 23 in the order of the evaporator 5 and the condenser 3 from upstream to downstream in the air flow.

[0021] In the air passage 23, the air sucked into the interior of the housing 20 from outside the housing 20 through the suction port 21 passes through the evaporator 5 and the condenser 3 in sequence, and is blown out of the housing 20 through the blowout port 22.

[0022] In the dehumidifying device 1, members constituting the refrigerant circuit may be arranged in the air passage 23 in addition to the condenser 3, the evaporator 5, and the blower 6. For example, a pressure reducing device 4 may be arranged in the air passage 23.

[0023] When the dehumidifying device 1 is installed indoors, the room may be cooled by dissipating the heat of the condenser 3 to the outside. For this heat dissipation to the outside, the device may be mounted on the exhaust duct equipment and the device itself may be installed on the window side.

[0024] The drain pan 7 is configured such that the dehumidified water condensed on the evaporator 5 is drained into the drain pan 7. In the present embodiment, the evaporator 5 and the condenser 3 are disposed on the drain pan 7.

[0025] Subsequently, with reference to FIGS. 3 to 16, the configurations of the evaporator 5 and the condenser 3 will be described in detail. FIG. 3 is a cross-sectional view of the evaporator 5 and the condenser 3 according to Embodiment 1 in a cross-section orthogonal to the stacking direction of the plurality of fins 11 of the condenser 3. In FIG. 3, for convenience of explanation, a part of the evaporator 5 and the condenser 3 is shown.

[0026] In the dehumidifying apparatus 1 according to the present embodiment, the condenser 3 has a plurality of fins (first fins) 11 and heat transfer tubes (first heat transfer tubes) 12. Each of the plurality of fins 11 is configured in a thin plate shape. The plurality of fins 11 are arranged so as to be stacked on one another. The heat transfer tubes 12 are arranged so as to penetrate through the plurality of stacked fins 11 in the stacking direction. The cross-sectional shape of the heat transfer tubes 12 is configured to extend in the row direction. Further, the heat transfer tubes 12 have a plurality of straight portions that linearly extend in the stacking direction of the plurality of fins 11. The condenser 3 also has a first header 31 and a second header 32 that connect the ends of the plurality of straight portions, respectively (see FIG. 4). Each of the plurality of straight portions of the heat transfer tubes 12 has a plurality of small-diameter pipe lines. The heat transfer tubes 12 are configured such that a refrigerant flows therethrough. The heat transfer tubes 12 of the condenser 3 are flat tubes. The heat transfer tubes 12 are flat tubes having a flat shape with respect to the flow direction of the air passing through the air passage 23. The cross-sectional shape of the heat transfer tubes 12 is configured to have a flat shape extending in the direction in which the condenser 3 and the evaporator 5 are arranged side by side.

[0027] FIG. 3 shows a cross-section in a cross-section orthogonal to the stacking direction of the plurality of fins 11 of the condenser 3. In the condenser 3, in the cross-section shown in FIG. 3, the straight portions of the plurality of heat transfer tubes 12 are arranged. The shapes of the straight portions of these plurality of heat transfer tubes 12 may be the same as each other.

[0028] In the present embodiment, the straight portions of these plurality of heat transfer tubes 12 are arranged in three or more rows in the step direction. Further, in the present embodiment, the straight portions of these plurality of heat transfer tubes 12 are arranged linearly in the step direction. That is, the centers of the straight portions of the plurality of heat transfer tubes 12 arranged in the step direction are arranged in a straight line. Also, the intervals between the straight portions of the heat transfer tubes 12 in each row may be the same as each other.

[0029] FIG. 4 is a front view of the condenser 3 when viewed from the column direction. The flat tubes of the condenser 3 extend in the horizontal direction. The shape of the fins 11 of the condenser 3 is a plate fin. The shape of the fins 11 of the condenser 3 is selected according to the performance of the condenser 3. The heat transfer tubes 12 of the condenser 3 include at least one refrigerant path (first refrigerant path). In the present embodiment, the number of refrigerant paths (first refrigerant paths) gradually decreases from the upstream to the downstream of the refrigerant flow.

[0030] Referring to FIGS. 2 and 4, the first header 31 has a refrigerant inlet and a refrigerant outlet. In the present embodiment, the refrigerant inlet of the first header 31 is connected by piping to the discharge port of the compressor 2. Also, the refrigerant outlet of the first header 31 is connected by piping to the inlet of the decompression device 4. By providing a partition 33 in the first header 31 and the second header 32, the refrigerant flowing in from the compressor 2 passes through a plurality of straight portions and repeatedly turns back between the first header 31 and the second header 32 a plurality of times, and then flows out from the refrigerant outlet of the first header 31 to the decompression device 4. At that time, it is preferable to gradually decrease the number of refrigerant paths of the straight portions reciprocating between the first header 31 and the second header 32 from the upstream side to the downstream side of the condenser 3. For example, if the number of refrigerant paths in the forward path from the first header 31 to the second header 32 is five, the number of refrigerant paths in the return path from the second header 32 to the first header 31 is preferably four or less.

[0031] Referring to FIG. 5, the shape of the fins 11 of the condenser 3 may be a corrugated fin. Also, as shown in FIG. 6, the first header 31 and the second header 32 may be divided. Thereby, the refrigerant flowing in from the compressor 2 may flow out from the refrigerant outlet of the condenser 3 to the decompression device 4 after folding back a plurality of times between the first header 31 and the second header 32 through a plurality of straight portions. The first header 31 includes a first header upstream portion 311 and a first header downstream portion 312 that are divided from each other. The second header 32 includes a second header upstream portion 321 and a second header downstream portion 322 that are divided from each other.

[0032] Also, the refrigerant outlet of the condenser 3 may be located in the second header 32 instead of the first header 31. In that case, the pipe connecting the decompression device 4 and the condenser 3 will be located on the opposite side of the pipe connecting the compressor 2 and the condenser 3 with the condenser 3 in between. Also, without providing the partition 33, the refrigerant flowing into the first header from the compressor 2 may flow out from the outlet of the second header 32 to the decompression device 4 without reciprocating between the first header 31 and the second header 32.

[0033] Also, as shown in FIG. 7, the heat transfer pipe 12 connected to the first header 31 has a plurality of curved portions in addition to a plurality of straight portions, and may be connected to the second header 32 after folding back a plurality of times between the first header 31 and the second header 32 with a plurality of straight portions and a plurality of curved portions.

[0034] Also, as shown in FIG. 8, the condenser 3 may not have the second header 32 and may have only the first header 31. In that case, the heat transfer pipe 12 has a plurality of straight portions and a plurality of curved portions, and folds back horizontally a plurality of times from the upstream side of the first header 31 and is connected to the downstream side of the first header 31.

[0035] FIG. 9 is a cross-sectional view of the evaporator 5 and the condenser 3 according to Embodiment 1 in a cross-section orthogonal to the stacking direction of the plurality of fins 13 of the evaporator 5. In FIG. 9, for convenience of explanation, a part of the evaporator 5 and the condenser 3 is shown.

[0036] The evaporator 5 has a plurality of fins (second fins) 13 and heat transfer tubes (second heat transfer tubes) 14. Each of the plurality of fins 13 is configured in a thin plate shape. The plurality of fins 13 are arranged so as to be stacked on one another. The heat transfer tubes 14 are arranged so as to penetrate through the plurality of fins 13 stacked on one another in the stacking direction. The cross-sectional shape of the heat transfer tube 14 is configured to extend in the row direction. Further, the heat transfer tube 14 has a plurality of straight portions that extend linearly in the stacking direction of the plurality of fins 13. Further, the evaporator 5 has a first header 34 and a second header 35 that respectively connect the ends of the plurality of straight portions (see FIG. 10). Each of the plurality of straight portions of the heat transfer tube 14 has a plurality of small-diameter pipe lines. The heat transfer tube 14 is configured such that a refrigerant flows therethrough. The heat transfer tube 14 of the evaporator 5 is a flat tube. The heat transfer tube 14 is a flat tube having a flat shape with respect to the flow direction of the air passing through the air passage 23. The cross-sectional shape of the heat transfer tube 14 is configured to have a flat shape extending in the direction in which the condenser 3 and the evaporator 5 are arranged side by side.

[0037] FIG. 9 shows a cross section in a cross section orthogonal to the stacking direction of the plurality of fins 13 of the evaporator 5. In the evaporator 5, in the cross section shown in FIG. 9, the straight portions of the plurality of heat transfer tubes 14 are arranged. The shapes of the straight portions of these heat transfer tubes 14 may be the same as each other.

[0038] In the present embodiment, the straight portions of the plurality of heat transfer tubes 14 are arranged in three or more rows in the step direction. Further, in the present embodiment, the straight portions of the plurality of heat transfer tubes 14 are arranged linearly in the step direction. That is, the centers of the straight portions of the plurality of heat transfer tubes 14 arranged in the step direction are arranged in a straight line. Further, the intervals between the straight portions of the heat transfer tubes 14 in each step may be the same as each other.

[0039] FIG. 10 is a front view of the evaporator 5 when viewed from the column direction. The flat tubes of the evaporator 5 extend in the vertical direction. The shape of the fins 13 of the evaporator 5 is a plate fin. The shape of the fins 13 of the evaporator 5 is selected according to the performance of the evaporator 5. The heat transfer tubes 14 of the evaporator 5 include at least one refrigerant path (second refrigerant path). In the present embodiment, the number of refrigerant paths (second refrigerant paths) gradually increases from the upstream to the downstream of the refrigerant flow.

[0040] Referring to FIGS. 2 and 10, the first header 34 has a refrigerant inlet and a refrigerant outlet. In the present embodiment, the refrigerant inlet of the first header 34 is connected to the outlet of the decompression device 4 by piping. Also, the refrigerant outlet of the first header 34 is connected to the suction port of the compressor 2 by piping. By providing a partition 36 in the first header 34 and the second header 35, the refrigerant flowing in from the decompression device 4 passes through a plurality of straight portions and repeatedly turns back between the first header 34 and the second header 35 a plurality of times, and then flows out from the refrigerant outlet of the first header 34 to the compressor 2. At that time, it is preferable to gradually increase the number of refrigerant paths of the straight portions reciprocating between the first header 34 and the second header 35 from the upstream side to the downstream side of the evaporator 5. For example, if the number of refrigerant paths in the forward path from the first header 34 to the second header 35 is 5, the number of refrigerant paths in the return path from the second header 35 to the first header 34 is preferably 6 or more.

[0041] Also, the positional relationship between the first header 34 and the second header 35 may be vertically reversed with the heat transfer tube 14 interposed therebetween. That is, the first header 34 may be on the upper side in the vertical direction with the second header 35 and the heat transfer tube 14 interposed therebetween.

[0042] Referring to FIG. 11, the fins 13 of the evaporator 5 may be corrugated fins. Also, the evaporator 5 may be a finless heat exchanger without the fins 13.

[0043] Also, as shown in FIG. 12, the first header 34 and the second header 35 may be divided. Thus, the refrigerant flowing in from the decompression device 4 may flow out from the outlet of the refrigerant of the evaporator 5 to the compressor 2 after turning back a plurality of times between the first header 34 and the second header 35 through a plurality of straight portions. The first header 34 includes a first header upstream portion 341 and a first header downstream portion 342 that are divided from each other. The second header 35 includes a second header upstream portion 351 and a second header downstream portion 352 that are divided from each other.

[0044] Also, the outlet of the refrigerant of the evaporator 5 may be located in the second header 35 instead of the first header 34. In that case, the pipe connecting the compressor 2 and the evaporator 5 will be located on the opposite side across the condenser 3 from the pipe connecting the compressor 2 and the condenser 3. Further, without providing the partition 36, the refrigerant flowing into the first header from the decompression device 4 may flow out from the outlet of the second header 35 to the compressor 2 without reciprocating between the first header 34 and the second header 35.

[0045] Also, as shown in FIG. 13, the heat transfer pipe 14 connected to the first header 34 has a plurality of curved portions in addition to a plurality of straight portions, and may be connected to the second header 35 after turning back a plurality of times between the first header 34 and the second header 35 with a plurality of straight portions and a plurality of curved portions.

[0046] Also, as shown in FIG. 14, the evaporator 5 may not have the second header 35 and may have only the first header 34. In that case, the heat transfer pipe 14 has a plurality of straight portions and a plurality of curved portions, turns back the vertical direction a plurality of times from the upstream side of the first header 34, and is connected to the downstream side of the first header 34.

[0047] Further, as shown in FIGS. 15 and 16, the fins 13 of the evaporator 5 may be configured to extend parallel and integrally with the straight portion of the heat transfer tube 14 and to extend in the row direction. FIG. 15 is a cross-sectional view in a cross-section orthogonal to the stacking direction of the plurality of fins 11 of the condenser 3. The fins 13 extend in the same direction as and integrally with the heat transfer tube 14 extending in the stage direction. Further, the fins 13 also extend in the row direction. The fins 13 may be such integral fins. The shape of the fins 13 of the evaporator 5 is selected according to the performance of the evaporator 5.

[0048] Next, with reference to FIGS. 1 and 2, the operation during the dehumidifying operation of the dehumidifying device 1 according to Embodiment 1 will be described.

[0049] The refrigerant in a superheated gas state discharged from the compressor 2 flows into the condenser 3 disposed in the air passage 23. The refrigerant in a superheated gas state that has flowed into the condenser 3 flows into the air passage 23 from the external space through the suction port 21, and is cooled by exchanging heat with the air that has passed through the evaporator 5 disposed in the air passage 23, becoming a refrigerant in a gas-liquid two-phase state, and is further cooled to become a refrigerant in a subcooled liquid state.

[0050] On the other hand, the air that passes through the condenser 3 disposed in the air passage 23 is heated by exchanging heat with the refrigerant in a superheated gas state or a gas-liquid two-phase state in the condenser 3 after passing through the evaporator 5 also disposed in the air passage 23.

[0051] The refrigerant in a subcooled liquid state that has flowed out of the condenser 3 is depressurized by passing through the decompression device 4, becomes a refrigerant in a gas-liquid two-phase state, and then flows into the evaporator 5 disposed in the air passage 23. The refrigerant in a gas-liquid two-phase state that has flowed into the evaporator 5 is heated by exchanging heat with the air taken into the air passage 23 from the suction port 21, becoming a refrigerant in a superheated gas state. This refrigerant in a superheated gas state is sucked into the compressor 2, compressed by the compressor 2, and discharged again.

[0052] On one hand, the air passing through the evaporator 5 disposed in the air passage 23 is taken into the air passage 23 from the suction port 21, and then heat - exchanges with the refrigerant in a gas - liquid two - phase state in the evaporator 5 and is dehumidified by being cooled to a temperature below the dew point of the air.

[0053] Next, the operation and effect of the dehumidifying device 1 according to Embodiment 1 will be described in comparison with a comparative example. FIG. 17 is a cross - sectional view in the stage direction of the evaporator 5 and the condenser 3 of the dehumidifying device 1 according to the comparative example. In order to improve the performance of the evaporator 5, the heat transfer tube 14 of the evaporator 5 is a flat tube having better heat transfer performance than a circular tube. However, generally, in a flat tube in which the heat transfer tube 14 of the evaporator 5 has a flat shape, dehumidified water tends to stay on the surface of the flat tube, and the staying dehumidified water hinders the heat exchange between the refrigerant and the air inside the flat tube. As a result, the dehumidification capacity of the dehumidifying device 1 decreases. Therefore, in the dehumidifying device 1 according to the comparative example, it is impossible to improve the dehumidification capacity while improving the performance of the evaporator 5.

[0054] According to the dehumidifying device 1 according to the present embodiment, the heat transfer tube 14 of the evaporator 5 is a flat tube. Therefore, the performance of the evaporator can be improved. The heat transfer tube 14 of the evaporator 5 extends in the vertical direction. Therefore, it is possible to suppress the dehumidified water from staying on the surface of the heat transfer tube 14. As a result, the drainage performance of the evaporator 5 can be improved. For this reason, it is possible to suppress the dehumidified water staying in the heat transfer tube 14 of the evaporator 5 from hindering the heat exchange between the refrigerant flowing in the heat transfer tube 14 and the air. Therefore, the heat transfer performance of the evaporator 5 can be improved. Thus, the dehumidification capacity of the dehumidifying device 1 can be improved.

[0055] Also, by suppressing the dehumidified water from staying on the surface of the heat transfer tube 14 of the evaporator 5, it is possible to suppress the increase in ventilation resistance caused by the staying dehumidified water narrowing the gaps between the heat transfer tubes 14 or between the fins 13. Therefore, since the input of the blower 6 can be reduced, the input of the dehumidifying device 1 can be reduced.

[0056] Further, the heat transfer tubes 12 of the condenser 3 extend in the horizontal direction. The heat transfer tubes 14 of the evaporator 5 extend in the vertical direction. Therefore, the heat transfer tubes 12 of the condenser 3 intersect the heat transfer tubes 14 of the evaporator 5. Accordingly, the air that has passed through the heat transfer tubes 14 of the evaporator 5 can be surely made to flow to the heat transfer tubes 12 of the condenser 3. Thus, the heat exchange efficiency between the air and the refrigerant in the condenser 3 can be improved.

[0057] Moreover, by improving the drainage performance, the dehumidified water condensed on the evaporator 5 is quickly drained to the drain pan 7, thereby reducing the amount of dehumidified water that scatters from the evaporator 5 to the condenser 3 and stays there. For this reason, it is possible to suppress the reheating of the air by the dehumidified water staying in the condenser 3 being heated and evaporated by the refrigerant flowing through the condenser 3. Thus, the dehumidifying amount of the dehumidifying device 1 can be further improved.

[0058] Further, according to the dehumidifying device 1 according to the present embodiment, in the condenser 3, the number of refrigerant paths (first refrigerant paths) gradually decreases from the upstream to the downstream of the refrigerant flow. That is, in the condenser 3, the number of refrigerant paths in the straight portion that reciprocates between the first header 31 and the second header 32 gradually decreases from the upstream side to the downstream side. Since the gaseous refrigerant on the upstream side has a larger pressure loss than the refrigerant in the gas-liquid two-phase state, for the gaseous refrigerant on the upstream side, the pressure loss can be reduced by decreasing the flow velocity by increasing the number of refrigerant paths. Also, since the refrigerant in the gas-liquid two-phase state on the downstream side has a smaller pressure loss than the gaseous refrigerant, for the refrigerant in the gas-liquid two-phase state on the downstream side, the heat transfer rate can be improved by increasing the flow velocity by decreasing the number of refrigerant paths.

[0059] Further, according to the dehumidifying device 1 according to the present embodiment, in the evaporator 5, the number of refrigerant paths (second refrigerant paths) gradually increases from the upstream to the downstream of the refrigerant flow. That is, in the evaporator 5, the first header 3 4 and the second header 3 5The number of refrigerant paths in the straight portion that reciprocates increases gradually from the upstream side to the downstream side. Since the refrigerant in the gas-liquid two-phase state on the upstream side has a smaller pressure loss than the gaseous refrigerant, the heat transfer coefficient can be improved by increasing the flow velocity by reducing the number of refrigerant paths for the refrigerant in the gas-liquid two-phase state on the upstream side. Also, since the gaseous refrigerant on the downstream side has a larger pressure loss than the refrigerant in the gas-liquid two-phase state, the pressure loss can be reduced by decreasing the flow velocity by increasing the number of refrigerant paths for the gaseous refrigerant on the downstream side.

[0060] Embodiment 2. With reference to FIGS. 18 to 20, the dehumidifying device 1 according to Embodiment 2 will be described. The dehumidifying device 1 according to the present embodiment is different from the dehumidifying device 1 according to Embodiment 1 in that it includes a first condensing portion 3a, a second condensing portion 3b, a first suction port 21a, a second suction port 21b, a partition portion 8, a first air passage 23a, and a second air passage 23b.

[0061] As shown in FIGS. 18 and 19, in the dehumidifying device 1 according to the present embodiment, the housing 20 has a first suction port 21a, a second suction port 21b, a first air passage 23a, and a second air passage 23b. The first suction port 21a is for taking in air. The first air passage 23a is configured to communicate with the first suction port 21a. The second suction port 21b is for taking in air. The second air passage 23b communicates with the second suction port 21b. The second air passage 23b is partitioned from the first air passage 23a.

[0062] As shown in FIGS. 19 and 20, in the dehumidifying device 1 according to the present embodiment, the condenser 3 includes a first condensing portion 3a and a second condensing portion 3b. The condenser 3 is configured such that the refrigerant flows in the order of the second condensing portion 3b and the first condensing portion 3a. The first condensing portion 3a is connected to the second condensing portion 3b. The refrigerant circuit 101 is configured to circulate the refrigerant in the order of the compressor 2, the second condensing portion 3b, the first condensing portion 3a, the decompression device 4, and the evaporator 5. The heat transfer tubes 12 of the condenser 3 include the heat transfer tubes 12a of the first condensing portion 3a and the heat transfer tubes 12b of the second condensing portion 3b.

[0063] The second condenser 3b is configured to condense and cool the refrigerant pressurized by the compressor 2. The second condenser 3b is a heat exchanger that performs heat exchange between the refrigerant and air. The second condenser 3b has a plurality of fins 11b and heat transfer tubes 12b. The second condenser 3b has an inlet and an outlet for the refrigerant, and an inlet and an outlet for air. In the present embodiment, the inlet and the outlet for the refrigerant of the second condenser 3b are respectively connected by pipes to the discharge port of the compressor 2 and the inlet for the refrigerant of the first condenser 3a. The heat transfer tube 12b of the second condenser 3b is a flat tube.

[0064] The first condenser 3a is configured to further condense and cool the refrigerant cooled by the second condenser 3b. The first condenser 3a is a heat exchanger that performs heat exchange between the refrigerant and air. The first condenser 3a has a plurality of fins 11a and heat transfer tubes 12a. The first condenser 3a has an inlet and an outlet for the refrigerant, and an inlet and an outlet for air. In the present embodiment, the inlet and the outlet for the refrigerant of the first condenser 3a are respectively connected by pipes to the outlet of the second condenser 3b and the inlet of the decompression device 4. The heat transfer tube 12a of the first condenser 3a is a flat tube.

[0065] In the present embodiment, the first condenser 3a and the second condenser 3b are flat tube heat exchangers having fins and heat transfer tubes of the same shape. The second condenser 3b is located above the first condenser 3a in the step direction.

[0066] In the first air passage 23a, an evaporator 5, a first condenser 3a, and a blower 6 are arranged. The evaporator 5 and the first condenser 3a are arranged in the first air passage 23a such that the air taken in from the first suction port 21a flows through the evaporator 5 and the first condenser 3a in this order. In the second air passage 23b, a second condenser 3b and a blower 6 are arranged. The second condenser 3b is arranged in the second air passage 23b such that the air taken in from the second suction port 21b flows through it.

[0067] In the present embodiment, the front area of the condenser 3 is larger than the front area of the evaporator 5. Specifically, the front area of the condenser 3 is larger than the front area of the evaporator 5 on the upper side in the step direction.

[0068] Note that the front area of the condenser 3 may be larger than the front area of the evaporator 5 in the product width direction of the fins 11 of the condenser 3.

[0069] The first suction port 21a and the second suction port 21b are provided to introduce air from the external space (indoor space) into the housing 20. The first air passage 23a is configured to connect the first suction port 21a and the air outlet 22. The second air passage 23b is configured to connect the second suction port 21b and the air outlet 22.

[0070] In the present embodiment, as the fan 6b rotates about the axis 6a, the air taken in from the external space (indoor space) as indicated by the arrow A in the figure passes through the evaporator 5 and the first condensing portion 3a as indicated by the arrow B in the figure within the first air passage 23a. Further, as the fan 6b rotates about the axis 6a, the air taken in from the external space (indoor space) as indicated by the arrow A' in the figure passes through the second condensing portion 3b as indicated by the arrow B' in the figure within the second air passage 23b. The air that has passed through the first air passage 23a and the air that has passed through the second air passage 23b are mixed with each other and discharged to the external space (indoor space) of the housing 20 through the air outlet 22.

[0071] The first air passage 23a and the second air passage 23b may be separated. The first air passage 23a and the second air passage 23b may be separated by, for example, a partition portion 8. Each of the first air passage 23a and the second air passage 23b is formed by, for example, the housing 20 and the partition portion 8. In the air flow direction within the second air passage 23b, one end located upstream of the partition portion 8 is formed at least upstream of the air outlet of the evaporator 5. In the above-mentioned flow direction, the other end located downstream of the partition portion 8 is formed at least downstream of the air inlet of the evaporator 5. The partition portion 8 is formed in a flat plate shape, for example. The partition portion 8 is fixed inside the housing 20.

[0072] According to the dehumidifying device 1 according to this embodiment, the evaporator 5 and the first condensation part 3a are arranged in the first air passage 23a such that the air taken in from the first suction port 21a flows through the evaporator 5 and the first condensation part 3a in this order. The second condensation part 3b is arranged in the second air passage 23b such that the air taken in from the second suction port 21b flows therethrough. Therefore, the air volume of the air flowing through the entire condenser 3 can be made larger than the air volume of the air flowing through the evaporator 5. By increasing the air volume of the entire condenser 3, the heat transfer performance on the condenser 3 side can be improved, so that the condensation temperature of the refrigerant can be lowered. Further, by lowering the condensation temperature, the difference between the condensation pressure and the evaporation pressure in the refrigerant circuit can be reduced, so that the input to the compressor 2 can be lowered. Thereby, the EF (Energy Factor) value (L / kWh) indicating the dehumidification amount L per 1 kWh, which is an index indicating the dehumidification performance of the dehumidifying device 1, can be improved.

[0073] Further, the material constituting the partition part 8 may be a material having a lower thermal conductivity than the materials constituting the heat transfer tubes, fins, and headers through which the refrigerant flows in the evaporator 5. Thereby, heat exchange between the air in the first air passage 23a and the air in the second air passage 23b via the partition part 8 can be reduced.

[0074] Embodiment 3. With reference to FIGS. 21 to 23, the dehumidifying device 1 according to Embodiment 3 will be described. The dehumidifying device 1 according to this embodiment is different from the dehumidifying device 1 according to Embodiment 2 in that it includes a third condensation part 3c.

[0075] As shown in FIGS. 21 and 22, in the dehumidifying device 1 according to the present embodiment, the condenser 3 includes a first condensation part 3a, a second condensation part 3b, and a third condensation part 3c. The condenser 3 is configured such that the refrigerant flows in the order of the second condensation part 3b, the first condensation part 3a, and the third condensation part 3c. The third condensation part 3c is connected to the second condensation part 3b. The refrigerant circuit 101 is configured to circulate the refrigerant in the order of the compressor 2, the first condensation part 3a, the second condensation part 3b, the third condensation part 3c, the decompression device 4, and the evaporator 5. The heat transfer tube 12 of the condenser 3 includes the heat transfer tube 12c of the third condensation part 3c.

[0076] The first condensation part 3a is arranged downstream of the third condensation part 3c in the air flow generated by the blower 6. That is, the first condensation part 3a is arranged downstream of the third condensation part 3c.

[0077] As shown in FIGS. 22 and 23, the third condensation part 3c is configured to further condense and cool the refrigerant cooled by the second condensation part 3b. The third condensation part 3c is a heat exchanger that performs heat exchange between the refrigerant and the air. The third condensation part 3c has a plurality of fins 11c and heat transfer tubes 12c. The third condensation part 3c has an inlet and an outlet for the refrigerant, and an inlet and an outlet for the air. In the present embodiment, the inlet and the outlet for the refrigerant of the third condensation part 3c are respectively connected by pipes to the outlet of the second condensation part 3b and the inlet of the decompression device 4. The third condensation part 3c is arranged upstream of the first condensation part 3a in the air flow generated by the blower 6. That is, the third condensation part 3c is arranged upstream of the first condensation part 3a. Also, the third condensation part 3c is arranged downstream of the evaporator 5 in the air flow generated by the blower 6. That is, the third condensation part 3c is arranged downstream of the evaporator 5. The heat transfer tube 12c of the third condensation part 3c is a flat tube.

[0078] In this embodiment, the first condensation section 3a, the second condensation section 3b, and the third condensation section 3c are flat-tube heat exchangers having fins and heat transfer tubes of the same shape. The front areas of the first condensation section 3a and the second condensation section 3b are larger than the front area of the third condensation section 3c on the upper side in the stage direction. The front area of the third condensation section 3c may be equivalent to that of the evaporator 5.

[0079] In the first air passage 23a, the evaporator 5, the first condensation section 3a, the third condensation section 3c, and the blower 6 are arranged. The evaporator 5, the first condensation section 3a, and the third condensation section 3c are arranged in the first air passage 23a such that the air taken in from the first suction port 21a flows through the evaporator 5, the third condensation section 3c, and the first condensation section 3a in this order. In the second air passage 23b, the second condensation section 3b and the blower 6 are arranged. The second condensation section 3b is arranged in the second air passage 23b such that the air taken in from the second suction port 21b flows through it.

[0080] In this embodiment, as the fan 6b rotates about the shaft 6a, the air taken in from the external space (indoor space) as indicated by the arrow A in the figure passes through the evaporator 5, the third condensation section 3c, and the first condensation section 3a as indicated by the arrow B in the figure within the first air passage 23a. Also, as the fan 6b rotates about the shaft 6a, the air taken in from the external space (indoor space) as indicated by the arrow A' in the figure passes through the second condensation section 3b as indicated by the arrow B' in the figure within the second air passage 23b. The air that has passed through the first air passage 23a and the air that has passed through the second air passage 23b mix with each other and are discharged to the external space (indoor space) of the housing 20 through the air outlet 22.

[0081] In the air flow direction within the second air passage 23b, one end located upstream of the partition portion 8 is formed at least upstream of the air outlet of the evaporator 5. In the above-mentioned flow direction, the other end located downstream of the partition portion 8 is formed at least downstream of the air inlet of the third condensation section 3c.

[0082] According to the dehumidifying device 1 according to the present embodiment, the evaporator 5, the first condensing section 3a, and the third condensing section 3c are arranged in the first air passage 23a so that the air taken in from the first suction port 21a flows through the evaporator 5, the third condensing section 3c, and the first condensing section 3a in this order. The second condensing section 3b is arranged in the second air passage 23b so that the air taken in from the second suction port 21b flows through it. Therefore, by combining the first condensing section 3a, the second condensing section 3b, and the third condensing section 3c, the heat transfer area of the entire condenser 3 can be increased. Thus, by increasing the heat transfer area of the entire condenser 3, the heat transfer performance on the condenser 3 side can be further improved, so that the condensation temperature of the refrigerant can be lowered. Also, by lowering the condensation temperature, the difference between the condensation pressure and the evaporation pressure in the refrigerant circuit can be reduced, so that the input to the compressor 2 can be decreased. As a result, the EF (Energy Factor) value (L / kWh) indicating the dehumidification amount L per 1 kWh, which is an index showing the dehumidification performance of the dehumidifying device 1, can be improved.

[0083] Further, the material constituting the partition portion 8 may be a material having a lower thermal conductivity than the materials constituting the heat transfer tubes, fins, and headers through which the refrigerant flows in the evaporator 5 and the third condensing section 3c. Thereby, heat exchange between the air in the first air passage 23a and the air in the second air passage 23b via the partition portion 8 can be reduced.

[0084] The above embodiments can be combined as appropriate. The embodiments disclosed this time should be considered as illustrative in all respects and not restrictive. The scope of the present disclosure is shown not by the above description but by the claims, and it is intended that all modifications within the meaning and scope equivalent to the claims are included.

Explanation of Reference Numerals

[0085] 1 Dehumidifying device, 2 Compressor, 3 Condenser, 3a First condensation section, 3b Second condensation section, 3c Third condensation section, 4 Pressure reducing device, 5 Evaporator, 6 Blower, 7 Drain pan, 8 Partition section, 11, 11a, 11b, 13 Fins, 12, 12a, 12b, 14 Heat transfer tubes, 20 Housing, 21 Suction port, 21a First suction port, 21b Second suction port, 22 Outlet, 23 Air passage, 23a First air passage, 23b Second air passage, 31, 34 First header, 32, 35 Second header, 33, 36 Partition, 101 Refrigerant circuit.

Claims

1. A housing, and a blower and a refrigerant circuit disposed within the housing, wherein the blower is configured to blow air, the refrigerant circuit has a compressor, a condenser, a decompression device, and an evaporator, and is configured to circulate refrigerant in the order of the compressor, the condenser, the decompression device, and the evaporator, the condenser has a first heat transfer tube through which the refrigerant flows, the evaporator has a second heat transfer tube through which the refrigerant flows, the condenser is disposed downstream of the evaporator with respect to the wind direction, the first heat transfer tube of the condenser is a flat tube and extends in the horizontal direction, the second heat transfer tube of the evaporator is a flat tube and extends in the vertical direction, the cross-sectional shape of the first heat transfer tube is configured to have a flat shape extending in the direction in which the condenser and the evaporator are arranged side by side, the cross-sectional shape of the second heat transfer tube is configured to have a flat shape extending in the direction in which the condenser and the evaporator are arranged side by side, a dehumidifying device.

2. the first heat transfer tube of the condenser includes at least one first refrigerant path, the number of the first refrigerant paths gradually decreases from the upstream to the downstream of the refrigerant flow, the second heat transfer tube of the evaporator includes at least one second refrigerant path, the number of the second refrigerant paths gradually increases from the upstream to the downstream of the refrigerant flow, the dehumidifying device according to Claim 1.

3. the housing has a first suction port for taking in the air, a first air passage communicating with the first suction port, a second suction port for taking in the air, and a second air passage communicating with the second suction port and partitioned from the first air passage, the condenser has a first condensation part and a second condensation part, and is configured such that the refrigerant flows in the order of the second condensation part and the first condensation part, the evaporator and the first condensation part are disposed in the first air passage such that the air taken in from the first suction port flows through the evaporator and the first condensation part in this order, the second condensation part is disposed in the second air passage such that the air taken in from the second suction port flows through it, the dehumidifying device according to Claim 1 or 2.

4. the condenser has a third condensation part, and is configured such that the refrigerant flows in the order of the second condensation part, the first condensation part, and the third condensation part, The evaporator, the first condensing section, and the third condensing section are arranged in the first air passage such that the air taken in from the first suction port flows in the order of the evaporator, the first condensing section, and the third condensing section. The dehumidifying apparatus according to claim 3, wherein the second condensing section is arranged in the second air passage such that the air taken in from the second suction port flows therethrough.

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