CN117157133A - Dehumidifying device - Google Patents

Abstract

The dehumidifying device includes a housing, a blower, and a refrigerant circuit. The blower and the refrigerant circuit are disposed within the housing. The air blower is configured to blow air. The refrigerant circuit has a compressor, a condenser (3), a pressure reducing device, and an evaporator (5), and is configured to circulate a refrigerant in the order of the compressor, the condenser (3), the pressure reducing device, and the evaporator (5). The condenser (3) has a 1 st heat transfer pipe (12) through which a refrigerant flows. The evaporator (5) has a 2 nd heat transfer pipe (14) through which the refrigerant flows. The condenser (3) is disposed downstream of the evaporator (5). The 1 st heat transfer pipe (12) of the condenser (3) is a flat pipe and extends in the horizontal direction. The 2 nd heat transfer tube (14) of the evaporator (5) is a flat tube and extends in the vertical direction.

Description

Dehumidifying device

Technical Field

The present disclosure relates to a dehumidifying apparatus.

Background

Conventionally, a dehumidifier using flat tubes for heat transfer tubes has been proposed to improve the performance of heat exchangers. For example, international publication No. 2019/077744 (patent document 1) describes a dehumidifier using a flat tube as a heat transfer tube of a condenser. In the dehumidifying apparatus described in this document, a round tube is used as a heat transfer tube of an evaporator.

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 above-mentioned document, since a round tube is used for the heat transfer tube of the evaporator, it is difficult to improve the performance of the evaporator.

In the dehumidifying apparatus, dehumidified water is condensed on the surface of the evaporator. If the flat tube described in the above document is used for a heat transfer tube of an evaporator, dehumidification water is retained on the surface of the flat tube of the evaporator due to poor drainage property of the flat tube. The dehumidified water retained on the surfaces of the flat tubes of the evaporator hinders heat exchange between the refrigerant in the flat tubes and air, and therefore the heat transfer performance of the evaporator is lowered. Thereby, the dehumidifying amount of the dehumidifying apparatus is reduced.

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

Means for solving the problems

The dehumidifying device of the present disclosure includes a housing, a blower, and a refrigerant circuit. The blower and the refrigerant circuit are disposed within the housing. The air blower is configured to blow air. The refrigerant circuit has a compressor, a condenser, a pressure reducing device, and an evaporator, and is configured to circulate a refrigerant in the order of the compressor, the condenser, the pressure reducing device, and the evaporator. The condenser has a 1 st heat transfer pipe through which the refrigerant flows. The evaporator has a 2 nd heat transfer pipe through which the refrigerant flows. The condenser is disposed downstream of the evaporator. The 1 st heat transfer pipe of the condenser is a flat pipe and extends in the horizontal direction. The 2 nd heat transfer tube of the evaporator is a flat tube and extends in the vertical direction.

ADVANTAGEOUS EFFECTS OF INVENTION

According to the dehumidifying apparatus of the present disclosure, the 2 nd 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 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 evaporator and the condenser of the dehumidifier of embodiment 1, taken perpendicular to the stacking direction of the plurality of fins of the condenser.

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

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

Fig. 6 is a front view of a modification 2 of the condenser of the dehumidifier of embodiment 1.

Fig. 7 is a front view of modification 3 of the evaporator of the dehumidifier of embodiment 1.

Fig. 8 is a front view of modification 4 of the evaporator of the dehumidifier of embodiment 1.

Fig. 9 is a cross-sectional view of the evaporator and the condenser of the dehumidifier of embodiment 1, taken perpendicular to the stacking direction of the plurality of fins of the evaporator.

Fig. 10 is a front view of an evaporator of the dehumidifying apparatus of embodiment 1.

Fig. 11 is a front view of modification 1 of the evaporator of the dehumidifier of embodiment 1.

Fig. 12 is a front view of modification 2 of the evaporator of the dehumidifier of embodiment 1.

Fig. 13 is a front view of modification 3 of the evaporator of the dehumidifier of embodiment 1.

Fig. 14 is a front view of modification 4 of the evaporator of the dehumidifier of embodiment 1.

Fig. 15 is a front view of modification 5 of the evaporator of the dehumidifier of embodiment 1.

Fig. 16 is a cross-sectional view in the layer direction of modification 5 of the evaporator and a cross-section of the condenser perpendicular to the stacking direction of the plurality of fins of the evaporator of the dehumidifying apparatus of embodiment 1.

Fig. 17 is a cross-sectional view of an evaporator and a condenser of the dehumidifying apparatus of the comparative example of embodiment 1.

Fig. 18 is a refrigerant circuit diagram of the dehumidifying apparatus of embodiment 2.

Fig. 19 is a schematic diagram showing the structure of the dehumidifying device of embodiment 2.

Fig. 20 is a cross-sectional view of an evaporator and a condenser of the dehumidifying device of embodiment 2, the cross-section being perpendicular to the stacking direction of a plurality of fins of the condenser.

Fig. 21 is a refrigerant circuit diagram of the dehumidifying apparatus of embodiment 3.

Fig. 22 is a schematic diagram showing the structure of the dehumidifier of embodiment 3.

Fig. 23 is a cross-sectional view of an evaporator and a condenser of the dehumidifying device of embodiment 3, the cross-section being perpendicular to the stacking direction of a plurality of fins of the condenser.

Detailed Description

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

Embodiment 1

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

As shown in fig. 1 and 2, the dehumidification device 1 includes a refrigerant circuit 101, a blower 6, a drain pan 7, and a housing 20, and the refrigerant circuit 101 includes a compressor 2, a condenser 3, a pressure reducing device 4, and an evaporator 5. The refrigerant circuit 101, the blower 6, and the drain pan 7 are disposed in the casing 20. The case 20 faces an external space (indoor space) to be dehumidified by the dehumidifier 1.

The refrigerant circuit 101 is configured to circulate the refrigerant in the order of the compressor 2, the condenser 3, the pressure reducing device 4, and the evaporator 5. Specifically, the refrigerant circuit 101 is configured by connecting the compressor 2, the condenser 3, the pressure reducing device 4, and the evaporator 5 in this order with pipes. The refrigerant passes through the piping 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 labeled on the refrigerant circuit 101 indicate the flow of the refrigerant in the refrigerant circuit 101.

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 compressor 2 is configured to have a variable discharge capacity of the refrigerant, 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 an inlet and an outlet for refrigerant and an inlet and an outlet for air. The inlet of the refrigerant in the condenser 3 is connected to the discharge port of the compressor 2 through a pipe. The condenser 3 is disposed downstream of the evaporator 5 in the air flow generated by the blower 6. That is, the condenser 3 is disposed on the leeward side from the evaporator 5. The heat transfer tubes of the condenser 3 are flat tubes.

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 the refrigerant outlet of the condenser 3 and the refrigerant inlet of the evaporator 5 through pipes.

The evaporator 5 is configured to absorb heat from the refrigerant expanded by the decompression device 4, thereby evaporating the refrigerant. The evaporator 5 is a heat exchanger that exchanges heat between refrigerant and air. The evaporator 5 has an inlet and an outlet for refrigerant and an inlet and an outlet for air. The outlet of the refrigerant in the evaporator 5 is connected to the suction port of the compressor 2 through a pipe. The evaporator 5 is disposed upstream of the condenser 3 in the air flow generated by the blower 6. That is, the evaporator 5 is disposed on the windward side with respect to the condenser 3. The heat transfer tubes of the evaporator 5 are flat tubes.

The blower 6 is configured to blow air. The blower 6 is configured to take in air from the outside of the casing 20 to the inside and blow the air to the condenser 3 and the evaporator 5. Specifically, the blower 6 is configured to take in air from an external space (indoor space) into the casing 20, and to discharge the air to the outside of the casing 20 after passing through the evaporator 5 and the condenser 3.

In the present embodiment, the blower 6 includes a shaft 6a and a fan 6b that rotates around the shaft 6 a. The fan 6B rotates around the shaft 6a, and air taken in from the external space (indoor space) as indicated by an arrow a in the figure passes through the evaporator 5 and the condenser 3 in this order as indicated by an arrow B in the figure, and is 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 housing 20 is provided with: a suction port 21 for allowing air to enter the interior of the casing 20 from an external space (indoor space) to be dehumidified; and a blowout port 22 for blowout of air from the inside of the casing 20 to the outside space (indoor space). The casing 20 further includes an air passage (air passage) 23 connecting the suction port 21 and the discharge port 22. The evaporator 5, the condenser 3, and the blower 6 are disposed in the air passage 23. Therefore, the evaporator 5 and the condenser 3 are disposed in the same air passage 23. The evaporator 5 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.

In the air passage 23, air sucked into the casing 20 from the outside of the casing 20 through the suction port 21 passes through the evaporator 5 and the condenser 3 in this order, and is blown out of the casing 20 through the air outlet 22.

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

In the case where the dehumidifier 1 is installed indoors, the heat of the condenser 3 may be radiated outdoors to cool the indoor space. In order to perform this heat radiation outdoors, an exhaust pipe may be mounted on the equipment and the equipment itself may be installed on the window side.

The drain pan 7 is configured such that dehumidified water condensed at the evaporator 5 is discharged to the drain pan 7. In the present embodiment, the evaporator 5 and the condenser 3 are disposed above the drain pan 7.

Next, the structures of the evaporator 5 and the condenser 3 will be described in detail with reference to fig. 3 to 16. Fig. 3 is a cross-sectional view of the evaporator 5 and the condenser 3 of embodiment 1, taken perpendicular to the stacking direction of the plurality of fins 11 of the condenser 3. In fig. 3, for convenience of explanation, the evaporator 5 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 (1 st fin) 11 and a heat transfer tube (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 in a stacked manner with each other. The heat transfer pipe 12 is disposed so as to penetrate the plurality of fins 11 stacked on 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 extending linearly in the stacking direction of the plurality of fins 11. The condenser 3 has a 1 st head 31 and a 2 nd head 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 tubes 12 of the condenser 3 are flat tubes. 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 evaporator 5 are arranged.

Fig. 3 shows a cross-sectional view of a section perpendicular 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, a plurality of straight portions of the 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 pipes 12 are arranged so as to be aligned in the layer direction by 3 layers or more. In the present embodiment, the linear portions of the plurality of heat transfer tubes 12 are arranged in a linear arrangement in the layer direction. That is, the centers of the straight portions of the plurality of heat transfer pipes 12 arranged in the layer direction are arranged on a straight line. Further, the intervals between the straight portions of the heat transfer pipes 12 of the respective layers 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 extend in the horizontal direction. The fins 11 of the condenser 3 are shaped as plate fins. The shape of the fins 11 of the condenser 3 is selected according to the performance of the condenser 3. The heat transfer pipe 12 of the condenser 3 includes at least 1 refrigerant path (1 st refrigerant path). In the present embodiment, the number of refrigerant paths (1 st refrigerant path) gradually decreases from the upstream toward the downstream of the flow of the refrigerant.

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

Referring to fig. 5, the fin 11 of the condenser 3 may be in the shape of a corrugated fin.

Further, as shown in fig. 6, the 1 st head 31 and the 2 nd head 32 may also be divided. Thus, the refrigerant flowing in from the compressor 2 may pass through the plurality of straight portions and turn back between the 1 st head 31 and the 2 nd head 32 a plurality of times, and then flow out from the refrigerant outlet of the condenser 3 to the pressure reducing device 4. The 1 st head 31 includes a 1 st head upstream portion 311 and a 1 st head downstream portion 312 that are divided from each other. The 2 nd head 32 includes a 2 nd head upstream portion 321 and a 2 nd head downstream portion 322 that are divided from each other.

The outlet of the refrigerant in the condenser 3 may be located not in the 1 st header 31 but in the 2 nd header 32. In this case, the piping connecting the pressure reducing device 4 and the condenser 3 and the piping connecting the compressor 2 and the condenser 3 are located on the opposite side with respect to the condenser 3. Further, the partition 33 may not be provided, and the refrigerant flowing from the compressor 2 into the 1 st head portion may flow out from the outlet of the 2 nd head portion 32 to the pressure reducing device 4 without reciprocating between the 1 st head portion 31 and the 2 nd head portion 32.

As shown in fig. 7, the heat transfer pipe 12 connected to the 1 st head 31 may have a plurality of bent portions in addition to a plurality of straight portions, and may be connected to the 2 nd head 32 after being folded back between the 1 st head 31 and the 2 nd head 32 by a plurality of straight portions and a plurality of bent portions.

As shown in fig. 8, the condenser 3 may have only the 1 st head 31 without the 2 nd head 32. In this case, the heat transfer pipe 12 has a plurality of straight portions and a plurality of bent portions, and is folded back a plurality of times in the horizontal direction from the upstream side of the 1 st head 31, and is connected to the downstream side of the 1 st head 31.

Fig. 9 is a cross-sectional view of the evaporator 5 and the condenser 3 of embodiment 1, taken perpendicular to the stacking direction of the plurality of fins 13 of the evaporator 5. In fig. 9, for convenience of explanation, the evaporator 5 and a part of the condenser 3 are illustrated.

The evaporator 5 has a plurality of fins (2 nd fins) 13 and heat transfer tubes (2 nd heat transfer tubes) 14. The plurality of fins 13 are each formed in a thin plate shape. The plurality of fins 13 are arranged in a stacked manner with each other. The heat transfer tubes 14 are disposed so as to penetrate the plurality of fins 13 stacked on each other in the stacking direction. The heat transfer pipe 14 is configured to have a cross-sectional shape extending in the column direction. The heat transfer tube 14 has a plurality of linear portions extending linearly in the stacking direction of the plurality of fins 13. The evaporator 5 has a 1 st head 34 and a 2 nd head 35 (see fig. 10) connecting the ends of the plurality of straight portions. The heat transfer pipe 14 has a plurality of straight portions each having a plurality of small-diameter pipes. The heat transfer pipe 14 is configured to flow a refrigerant. The heat transfer tubes 14 of the evaporator 5 are flat tubes. The heat transfer pipe 14 is a flat pipe having a flat shape with respect to the flow direction of the air passing through the air passage 23. The heat transfer pipe 14 is configured to have a flat shape extending in the direction in which the condenser 3 and the evaporator 5 are arranged.

Fig. 9 shows a cross-sectional view of a section perpendicular 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, straight portions of a plurality of heat transfer tubes 14 are arranged. The shape of the straight portions of these heat transfer pipes 14 may be the same as each other.

In the present embodiment, the straight portions of the plurality of heat transfer pipes 14 are arranged so as to be aligned in the layer direction by 3 layers or more. In the present embodiment, the linear portions of the plurality of heat transfer tubes 14 are arranged in a linear arrangement in the layer direction. That is, the centers of the straight portions of the plurality of heat transfer tubes 14 arranged in the layer direction are arranged on a straight line. Further, the intervals between the straight portions of the heat transfer pipes 14 of the respective layers may be the same as each other.

Fig. 10 is a front view of the evaporator 5 when the evaporator 5 is viewed from the column direction. The flat tubes of the evaporator 5 extend in the vertical direction. The fins 13 of the evaporator 5 are shaped as plate fins. The shape of the fins 13 of the evaporator 5 is selected according to the performance of the evaporator 5. The heat transfer pipe 14 of the evaporator 5 includes at least 1 refrigerant path (refrigerant path 2). In the present embodiment, the number of refrigerant paths (2 nd refrigerant paths) gradually increases from the upstream toward the downstream of the flow of the refrigerant.

Referring to fig. 2 and 10, the 1 st head 34 has an inlet for refrigerant and an outlet for refrigerant. In the present embodiment, the inlet of the refrigerant in the 1 st header 34 is connected to the outlet of the pressure reducing device 4 through a pipe. The outlet of the refrigerant in the 1 st header 34 is connected to the suction port of the compressor 2 through a pipe. By providing the partition 36 in the 1 st head 34 and the 2 nd head 35, the refrigerant flowing in from the pressure reducing device 4 is folded back between the 1 st head 34 and the 2 nd head 35 a plurality of times by a plurality of straight portions, and then flows out from the outlet of the 1 st head 34 to the compressor 2. At this time, the number of refrigerant paths in the straight line portion that reciprocates between the 1 st head 34 and the 2 nd head 35 preferably increases gradually from the upstream side toward the downstream side of the evaporator 5. For example, if the number of refrigerant paths going from the 1 st head 34 to the 2 nd head 35 is 5, the number of refrigerant paths going from the 2 nd head 35 to the 1 st head 34 is preferably 6 or more.

The positional relationship between the 1 st head 34 and the 2 nd head 35 may be reversed vertically through the heat transfer pipe 14. That is, the 1 st head 34 and the 2 nd head 35 may be located above in the vertical direction with the heat transfer pipe 14 interposed therebetween.

Referring to fig. 11, the fins 13 of the evaporator 5 may also be corrugated fins. The evaporator 5 may be a finless heat exchanger without the fins 13.

Further, as shown in fig. 12, the 1 st head 34 and the 2 nd head 35 may also be divided. Thus, the refrigerant flowing in from the pressure reducing device 4 can flow out from the outlet of the refrigerant of the evaporator 5 to the compressor 2 after being folded back between the 1 st head 34 and the 2 nd head 35 a plurality of times by the plurality of straight portions. The 1 st head 34 includes a 1 st head upstream portion 341 and a 1 st head downstream portion 342 that are divided from each other. The 2 nd head 35 includes a 2 nd head upstream portion 351 and a 2 nd head downstream portion 352 that are divided from each other.

The outlet of the refrigerant of the evaporator 5 may be located not in the 1 st head 34 but in the 2 nd head 35. In this case, the pipe connecting the compressor 2 and the evaporator 5 and the pipe connecting the compressor 2 and the condenser 3 are located on the opposite side with the condenser 3 interposed therebetween. Further, the partition 36 may not be provided, and the refrigerant flowing from the pressure reducing device 4 into the 1 st head may flow out from the outlet of the 2 nd head 35 to the compressor 2 without reciprocating between the 1 st head 34 and the 2 nd head 35.

As shown in fig. 13, the heat transfer pipe 14 connected to the 1 st head 34 may have a plurality of bent portions in addition to a plurality of straight portions, and may be connected to the 2 nd head 35 after being folded back between the 1 st head 34 and the 2 nd head 35 a plurality of times by a plurality of straight portions and a plurality of bent portions.

Further, as shown in fig. 14, the evaporator 5 may not have the 2 nd head 35, but may have only the 1 st head 34. In this case, the heat transfer pipe 14 has a plurality of straight portions and a plurality of bent portions, and is folded back a plurality of times in the vertical direction from the upstream side of the 1 st head 34, and is connected to the downstream side of the 1 st head 34.

As shown in fig. 15 and 16, the fins 13 of the evaporator 5 may be configured to extend integrally and parallel to the straight portions of the heat transfer tubes 14 and extend in the column direction. Fig. 15 is a cross-sectional view of a section perpendicular to the stacking direction of the plurality of fins 11 of the condenser 3. The fins 13 extend in the same direction with respect to the heat transfer tubes 14 extending in the layer direction, and are integrated. Further, the fins 13 also extend in the column 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.

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

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 into the air passage 23 from the outside space through the suction port 21 and passing through the evaporator 5 disposed in the air passage 23, and is cooled to become a gas-liquid two-phase refrigerant, and is further cooled to become a supercooled liquid refrigerant.

On the other hand, the air passing through the condenser 3 disposed in the air duct 23 passes through the evaporator 5 disposed in the air duct 23 as well, and then is heated by heat exchange with the superheated gas-state refrigerant or the gas-liquid two-phase refrigerant in the condenser 3.

The supercooled liquid refrigerant flowing out of the condenser 3 passes through the decompression device 4, is decompressed to be a gas-liquid two-phase refrigerant, and then flows into the evaporator 5 disposed in the air passage 23. The refrigerant flowing into the evaporator 5 in a gas-liquid two-phase state exchanges heat with the air taken into the air passage 23 from the suction port 21, and is heated to a 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, after the air passing through the evaporator 5 disposed in the air passage 23 is taken into the air passage 23 through the suction port 21, the air is heat-exchanged with the refrigerant in the gas-liquid two-phase state in the evaporator 5, cooled to a temperature equal to or lower than the dew point of the air, and dehumidified.

Next, the operation and effect of the dehumidifier 1 according to embodiment 1 will be described in comparison with a comparative example.

Fig. 17 is a sectional view of the evaporator 5 and the condenser 3 of the dehumidifying apparatus 1 of the comparative example in the layer direction. In order to improve the performance of the evaporator 5, the heat transfer pipe 14 of the evaporator 5 is a flat pipe having heat transfer performance superior to that of a round pipe. However, in general, in a flat tube in which the heat transfer tube 14 of the evaporator 5 is flat, the dehumidified water is likely to be retained on the surface of the flat tube, and the retained dehumidified water prevents heat exchange between the refrigerant and air in the flat tube. Thereby, the dehumidifying amount of the dehumidifying apparatus 1 is reduced. Therefore, in the dehumidifying apparatus 1 of the comparative example, the performance of the evaporator 5 cannot be improved and the dehumidifying amount cannot be improved.

According to the dehumidification device 1 of the present embodiment, the heat transfer tubes 14 of the evaporator 5 are flat tubes. Therefore, the performance of the evaporator can be improved. The heat transfer pipe 14 of the evaporator 5 extends in the vertical direction. Therefore, the dehumidification water can be suppressed from being retained on the surface of the heat transfer pipe 14. This can improve the drainage of the evaporator 5. Therefore, the dehumidified water retained in the heat transfer pipe 14 of the evaporator 5 can be suppressed from interfering with the heat exchange between the air and the refrigerant flowing through the heat transfer pipe 14. Therefore, the heat transfer performance of the evaporator 5 can be improved. Therefore, the dehumidifying amount of the dehumidifying apparatus 1 can be increased.

Further, by suppressing the stagnation of the dehumidified water on the surface of the heat transfer tubes 14 of the evaporator 5, it is possible to suppress the increase in ventilation resistance due to the narrowing of the gaps between the heat transfer tubes 14 or between the fins 13 by the retained dehumidified water. This can reduce the input of the blower 6, and thus the input of the dehumidifier 1 can be reduced.

Further, the heat transfer pipe 12 of the condenser 3 extends in the horizontal direction. The heat transfer pipe 14 of the evaporator 5 extends in the vertical direction. Therefore, the heat transfer pipe 12 of the condenser 3 intersects the heat transfer pipe 14 of the evaporator 5. Therefore, the air passing through the heat transfer pipe 14 of the evaporator 5 can be reliably made to flow to the heat transfer pipe 12 of the condenser 3. Therefore, the heat exchange efficiency between the air in the condenser 3 and the refrigerant can be improved.

In addition, by improving the drainage property, the dehumidified water condensed by the evaporator 5 is quickly drained to the drain pan 7, and thereby the amount of dehumidified water scattered from the evaporator 5 to the condenser 3 and retained can be reduced. Therefore, the dehumidified water retained in the condenser 3 can be suppressed from being heated and evaporated by the refrigerant flowing through the condenser 3, and the air can be re-humidified. Therefore, the dehumidifying amount of the dehumidifying apparatus 1 can be further increased.

Further, according to the dehumidifying device 1 of the present embodiment, in the condenser 3, the number of refrigerant paths (1 st refrigerant path) gradually decreases from the upstream toward the downstream of the flow of the refrigerant. That is, in the condenser 3, the number of refrigerant paths in the straight line portion that reciprocates between the 1 st head 31 and the 2 nd head 32 gradually decreases from the upstream side toward 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 pressure loss can be reduced by increasing the number of refrigerant paths for the refrigerant in the gas state on the upstream side and reducing the flow rate. 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 number of refrigerant paths is reduced for the refrigerant in the gas-liquid two-phase state on the downstream side, and the flow rate is increased, so that the heat transfer rate can be improved.

Further, according to the dehumidifying device 1 of the present embodiment, in the evaporator 5, the number of refrigerant paths (2 nd refrigerant path) gradually increases from the upstream toward the downstream of the flow of the refrigerant. That is, in the evaporator 5, the number of refrigerant paths in the straight line portion that reciprocates between the 1 st head 33 and the 2 nd head 34 gradually increases from the upstream side toward the downstream side. Since the pressure loss of the refrigerant in the gas-liquid two-phase state on the upstream side is smaller than the pressure loss of the refrigerant in the gas state, the number of refrigerant paths is reduced for the refrigerant in the gas-liquid two-phase state on the upstream side, and the flow rate is increased, whereby the heat transfer rate can be improved. Further, since the pressure loss of the refrigerant in the gas state on the downstream side is larger than the pressure loss of the refrigerant in the gas-liquid two-phase state, the pressure loss can be reduced by increasing the number of refrigerant paths for the refrigerant in the gas state on the downstream side to reduce the flow rate.

Embodiment 2

Referring to fig. 18 to 20, 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 1 st suction port 21a, a 2 nd suction port 21b, a partition 8, a 1 st air path 23a, and a 2 nd air path 23b.

As shown in fig. 18 and 19, 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 passage 23a, and a 2 nd air passage 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 passage 23b is partitioned from the 1 st air passage 23 a.

As shown in fig. 19 and 20, in the dehumidifying apparatus 1 of the present embodiment, the condenser 3 includes a 1 st condensation unit 3a and a 2 nd condensation unit 3b. The condenser 3 is configured to flow the refrigerant in the order of the 2 nd condensation unit 3b and the 1 st condensation unit 3a. The 1 st condensation unit 3a is connected to the 2 nd condensation unit 3b. The refrigerant circuit 101 is configured to circulate a refrigerant in the order of the compressor 2, the 2 nd condensation unit 3b, the 1 st condensation unit 3a, the pressure reducing device 4, and the evaporator 5. The heat transfer pipe 12 of the condenser 3 includes a heat transfer pipe 12a of the 1 st condensation unit 3a and a heat transfer pipe 12b of the 2 nd condensation unit 3b.

The 2 nd condensing unit 3b is configured to condense and cool the refrigerant boosted by the compressor 2. The 2 nd condensing unit 3b is a heat exchanger that exchanges heat between the refrigerant and air. The 2 nd condensing portion 3b has a plurality of fins 11b and heat transfer tubes 12b. The 2 nd condensing portion 3b has an inlet and an outlet for refrigerant and an inlet and an outlet for air. In the present embodiment, the inlet and outlet of the refrigerant in the 2 nd condensation unit 3b are connected to the discharge port of the compressor 2 and the inlet of the refrigerant in the 1 st condensation unit 3a through pipes, respectively. 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 3b. 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 unit 3a has an inlet and an outlet for refrigerant and an inlet and an outlet for air. In the present embodiment, the inlet and outlet of the refrigerant in 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, respectively, by pipes. The heat transfer tube 12a of the 1 st condensation unit 3a is a flat tube.

In the present embodiment, the 1 st condensation portion 3a and the 2 nd condensation portion 3b are flat tube heat exchangers having fins and heat transfer tubes of the same shape. The 2 nd condensation part 3b is located above the 1 st condensation part 3a in the layer direction.

The 1 st air passage 23a is provided with an evaporator 5, a 1 st condensation unit 3a, and a blower 6. The evaporator 5 and the 1 st condensation unit 3a are disposed in the 1 st air passage 23a so that the air taken in from the 1 st suction port 21a flows in the order of the evaporator 5 and the 1 st condensation unit 3a. The 2 nd condensation unit 3b and the blower 6 are disposed in the 2 nd air duct 23b. The 2 nd condensation unit 3b is disposed in the 2 nd air duct 23b such that the air taken in from the 2 nd suction port 21b flows through the 2 nd condensation unit 3b.

In the present embodiment, the front surface area of the condenser 3 is larger than the front surface area of the evaporator 5. Specifically, the front surface area of the condenser 3 is larger on the layer direction side than the front surface area of the evaporator 5.

The front surface area of the condenser 3 may be larger than the front surface area of the evaporator 5 in the stacking width direction of the fins 11 of the condenser 3.

The 1 st suction port 21a and the 2 nd suction port 21b are provided for allowing air to enter the inside of the casing 20 from an external space (indoor space). The 1 st air passage 23a is configured to connect the 1 st suction port 21a and the blowout port 22. The 2 nd air duct 23b is configured to connect the 2 nd suction port 21b and the blowout port 22.

In the present embodiment, the fan 6B rotates around the shaft 6a, and thereby air taken in from the outside space (indoor space) as indicated by arrow a in the figure passes through the evaporator 5 and the 1 st condensation unit 3a in the 1 st air passage 23a as indicated by arrow B in the figure. The fan 6B rotates around the shaft 6a, and thereby air taken in from the outside space (indoor space) as indicated by an arrow a 'passes through the 2 nd condensation unit 3B 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 path 23a and the 2 nd air path 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 evaporator 5. The other end of the partition 8 located downstream in the flow direction is formed at least at a position downstream of the air inlet of the evaporator 5. 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 dehumidifying apparatus 1 of the present embodiment, the evaporator 5 and the 1 st condensation unit 3a are disposed in the 1 st air path 23a such that the air taken in from the 1 st suction port 21a flows in the order of the evaporator 5 and the 1 st condensation unit 3a. The 2 nd condensation unit 3b is disposed in the 2 nd air duct 23b such that the air taken in from the 2 nd suction port 21b flows through the 2 nd condensation unit 3b. Therefore, the volume of air flowing through the entire condenser 3 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 reducing the condensation temperature, the difference between the condensation pressure and the evaporation pressure in the refrigerant circuit can be reduced, and therefore, the input to the compressor 2 can be reduced. This can increase the EF (Energy Factor) value (L/kWh) indicating the amount of dehumidification 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, fins, and heads through which the refrigerant flows in the evaporator 5. 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 via the partition 8.

Embodiment 3

Referring to fig. 21 to 23, a dehumidifying device 1 according to embodiment 3 will be described. The dehumidifying apparatus 1 of the present embodiment is different from the dehumidifying apparatus 1 of embodiment 2 in that the 3 rd condensing unit 3c is provided.

As shown in fig. 21 and 22, in the dehumidifying apparatus 1 of the present embodiment, the condenser 3 includes a 1 st condensation unit 3a, a 2 nd condensation unit 3b, and a 3 rd condensation unit 3c. The condenser 3 is configured to flow the refrigerant in the order of the 2 nd condensation unit 3b, the 1 st condensation unit 3a, and the 3 rd condensation unit 3c. The 3 rd condensing unit 3c is connected to the 2 nd condensing unit 3b. The refrigerant circuit 101 is configured to circulate a refrigerant in the order of the compressor 2, the 1 st condensation unit 3a, the 2 nd condensation unit 3b, the 3 rd condensation unit 3c, the pressure reducing device 4, and the evaporator 5. The heat transfer pipe 12 of the condenser 3 includes a heat transfer pipe 12c of the 3 rd condensation portion 3c.

The 1 st condensation unit 3a is disposed downstream of the 3 rd condensation unit 3c in the air flow generated by the blower 6. That is, the 1 st condensation unit 3a is disposed downstream of the 3 rd condensation unit 3c.

As shown in fig. 22 and 23, the 3 rd condensing unit 3c is configured to further condense and cool the refrigerant cooled by the 2 nd condensing unit 3b. 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 an inlet and an outlet for refrigerant and an inlet and an outlet for air. In the present embodiment, the inlet and outlet of the refrigerant in the 3 rd condensation unit 3c 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 3 rd condensing unit 3c is disposed upstream of the 1 st condensing unit 3a in the air flow generated by the blower 6. That is, the 3 rd condensation unit 3c is disposed upstream of the 1 st condensation unit 3a. The 3 rd condensing unit 3c is disposed downstream of the evaporator 5 in the air flow generated by the blower 6. That is, the 3 rd condensation unit 3c is disposed downstream of the evaporator 5. The heat transfer tube 12c of the 3 rd condensation unit 3c is a flat tube.

In the present embodiment, the 1 st condensation portion 3a, the 2 nd condensation portion 3b, and the 3 rd condensation portion 3c are flat tube heat exchangers having fins and heat transfer tubes of the same shape. The front surface areas of the 1 st condensation portion 3a and the 2 nd condensation portion 3b are larger on the layer direction side than the front surface area of the 3 rd condensation portion 3c. The front surface area of the 3 rd condensing portion 3c may also be identical to that of the evaporator 5.

The 1 st air passage 23a is provided with an evaporator 5, a 1 st condensation unit 3a, a 3 rd condensation unit 3c, and a blower 6. The evaporator 5, the 1 st condensation unit 3a, and the 3 rd condensation unit 3c 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 evaporator 5, the 3 rd condensation unit 3c, and the 1 st condensation unit 3a. The 2 nd condensation unit 3b and the blower 6 are disposed in the 2 nd air duct 23b. The 2 nd condensation unit 3b is disposed in the 2 nd air duct 23b such that the air taken in from the 2 nd suction port 21b flows through the 2 nd condensation unit 3b.

In the present embodiment, the fan 6B rotates around the shaft 6a, and thereby air taken in from the outside space (indoor space) as indicated by arrow a in the figure passes through the evaporator 5, the 3 rd condensation unit 3c, and the 1 st condensation unit 3a in the 1 st air path 23a as indicated by arrow B in the figure. The fan 6B rotates around the shaft 6a, and thereby air taken in from the outside space (indoor space) as indicated by an arrow a 'passes through the 2 nd condensation unit 3B 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.

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 evaporator 5. The other end of the partition 8 located downstream in the flow direction is formed at least at a position downstream of the air inlet of the 3 rd condensation unit 3c.

According to the dehumidifier 1 of the present embodiment, the evaporator 5, the 1 st condensation unit 3a, and the 3 rd condensation unit 3c are disposed in the 1 st air duct 23a such that the air taken in from the 1 st suction port 21a flows in the order of the evaporator 5, the 3 rd condensation unit 3c, and the 1 st condensation unit 3a. The 2 nd condensation unit 3b is disposed in the 2 nd air duct 23b such that the air taken in from the 2 nd suction port 21b flows through the 2 nd condensation unit 3b. Therefore, by combining the 1 st condensation unit 3a, the 2 nd condensation unit 3b, and the 3 rd condensation unit 3c, the heat transfer area of the entire condenser 3 can be increased. Therefore, by increasing the heat transfer area of the entire condenser 3, the heat transfer performance on the condenser 3 side can be further improved, and therefore, the condensing temperature of the refrigerant can be reduced. Further, by reducing the condensation temperature, the difference between the condensation pressure and the evaporation pressure in the refrigerant circuit can be reduced, and therefore, the input to the compressor 2 can be reduced. This can increase the EF (Energy Factor) value (L/kWh) indicating the amount of dehumidification 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, fins, and heads through which the refrigerant flows in the evaporator 5 and the 3 rd condensation unit 3c. This reduces the heat exchange between the air in the 1 st air passage 23a and the air in the 2 nd air passage 23b via the partition 8.

The above embodiments can be appropriately combined.

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

Description of the reference numerals

A dehumidifying device 1, a compressor 2, a condenser 3, a condensing unit 3a 1, a condensing unit 3b 2, a condensing unit 3c 3, a decompressing device 4, an evaporator 5, a blower 6, a drain pan 7, a partition 8, fins 11, 11a, 11b, 13, heat transfer pipes 12, 12a, 12b, 14, a 20 case, a 21 suction inlet, a 1 st suction inlet 21b 2 suction inlet, a 22 blow-out outlet 23, a 1 st air passage 23b 2 nd air passage 31, 341 st head, 32, 35 nd head, 33, 36 partition, and a 101 refrigerant circuit.

Claims (4)

1. A dehumidifying device, wherein,

the dehumidifying device is provided with:

a housing; and

a blower and a refrigerant circuit disposed in the housing,

the blower is configured to blow air,

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

the condenser has a 1 st heat transfer pipe through which the refrigerant flows,

the evaporator has a 2 nd heat transfer pipe through which the refrigerant flows,

the condenser is disposed downstream of the evaporator,

the 1 st heat transfer pipe of the condenser is a flat pipe, and extends in a horizontal direction,

the 2 nd heat transfer tube of the evaporator is a flat tube and extends in the vertical direction.

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

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

the number of the 1 st refrigerant paths gradually decreases from the upstream toward the downstream of the flow of the refrigerant,

the 2 nd heat transfer tube of the evaporator contains at least 12 nd refrigerant path,

the number of the 2 nd refrigerant paths gradually increases from the upstream toward the downstream of the flow of the 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 path communicating with the 1 st suction port, a 2 nd suction port for taking in the air, and a 2 nd air path communicating with the 2 nd suction port and spaced apart from the 1 st air path,

the condenser has a 1 st condensation part and a 2 nd condensation part, and is configured to flow the refrigerant circuit in the order of the 2 nd condensation part and the 1 st condensation part,

the evaporator and the 1 st condensation part are arranged in the 1 st air path, so that the air taken in from the 1 st suction inlet flows in the sequence of the evaporator and the 1 st condensation part,

the 2 nd condensing unit is disposed in the 2 nd air duct such that the air taken in from the 2 nd suction port flows through the 2 nd condensing unit.

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

the condenser has a 3 rd condensing portion and is configured to flow the refrigerant in the order of the 2 nd condensing portion, the 1 st condensing portion, and the 3 rd condensing portion,

the evaporator, the 1 st condensing unit and the 3 rd condensing unit are disposed in the 1 st air path so that the air taken in from the 1 st suction port flows in the order of the evaporator, the 1 st condensing unit and the 3 rd condensing unit,

the 2 nd condensing unit is disposed in the 2 nd air duct such that the air taken in from the 2 nd suction port flows through the 2 nd condensing unit.