JP7394722B2 - dehumidifier - Google Patents

Description

The present disclosure relates to a dehumidifier.

BACKGROUND ART Conventionally, in order to improve the performance of a condenser and reduce its size, a dehumidification device using a flat tube as a heat transfer tube of a condenser has been proposed. For example, International Publication No. 2019/077744 (Patent Document 1) describes a dehumidification device using a flat tube as a heat transfer tube of a condenser.

International Publication No. 2019/077744

In a dehumidifier, dehumidified water condenses on the surface of an evaporator. This dehumidified water scatters to a condenser placed on the leeward side of the evaporator. As described in the above-mentioned literature, when a flat tube is used as a heat exchanger tube of a condenser, dehumidified water stays on the surface of the flat tube. The dehumidified water that has accumulated on the surface of the flat tube is heated by the refrigerant inside the flat tube and evaporates, thereby rehumidifying the air. This reduces the amount of moisture removed by the dehumidifier.

The present disclosure has been made in view of the above problems, and its purpose is to provide a dehumidifier that can improve the performance of the condenser, reduce the size, and increase the amount of dehumidification. It is.

A dehumidifier according to the present disclosure includes a housing, a blower, and a refrigerant circuit. The blower and refrigerant circuit are located inside the housing. The blower is configured to blow air. The refrigerant circuit includes a compressor, a condenser, a pressure reducing device, and an evaporator, and is configured to circulate refrigerant in the order of the compressor, condenser, pressure reducing device, and evaporator. The condenser includes a first condensing section having a first heat exchanger tube through which a refrigerant flows, and a second condensing section having a second heat exchanger tube through which a refrigerant flows. The first condensing section is located downstream of the evaporator. The second condensing section is arranged on the leeward side of the first condensing section. The first heat exchanger tube of the first condensing section is a circular tube. The second heat exchanger tube of the second condensing section is a flat tube.

According to the present disclosure, the first heat exchanger tube of the first condensing section is a circular tube, and the second heat exchanger tube of the second condensing section is a flat tube. Therefore, the size of the condenser can be reduced while improving the performance of the condenser, and the amount of dehumidification can be improved.

FIG. 2 is a refrigerant circuit diagram of the dehumidification device according to the first embodiment. 1 is a schematic diagram showing the configuration of a dehumidifying device according to Embodiment 1. FIG. FIG. 3 is a cross-sectional view of an evaporator, a first condensing section, and a second condensing section of the dehumidification device according to the first embodiment. It is a front view of the 1st condensation part of the dehumidification device concerning Embodiment 1. FIG. 7 is a front view of a modification of the first condensing section of the dehumidification device according to the first embodiment. FIG. 3 is a cross-sectional view of an evaporator and a condenser of a dehumidification device according to a comparative example of the first embodiment. FIG. 2 is a refrigerant circuit diagram of a dehumidifier according to a second embodiment. FIG. 2 is a schematic diagram showing the configuration of a dehumidifying device according to Embodiment 2. FIG. FIG. 3 is a refrigerant circuit diagram of a dehumidifier according to a third embodiment. FIG. 3 is a schematic diagram showing the configuration of a dehumidifying device according to Embodiment 3. FIG. 7 is a cross-sectional view of an evaporator, a first condensing section, a second condensing section, and a third condensing section of a dehumidifying device according to a third embodiment. FIG. 7 is a cross-sectional view of an evaporator, a first condensing section, a second condensing section, and a third condensing section of a dehumidifying device according to a fourth embodiment.

Embodiments will be described below with reference to the drawings. In addition, in the drawings, the same or corresponding parts are given the same reference numerals, and the description thereof will not be repeated.

Embodiment 1.
The configuration of the dehumidifier 1 according to the first embodiment will be described with reference to FIGS. 1 and 2. FIG. 1 is a refrigerant circuit diagram of a dehumidifier 1 according to the first embodiment. FIG. 2 is a schematic diagram showing the configuration of the dehumidifier 1 according to the first embodiment.

As shown in FIGS. 1 and 2, the dehumidifier 1 includes a refrigerant circuit 10 having a compressor 2, a condenser 3, a pressure reducing device 4, and an evaporator 5, a blower 6, a drain pan 7, and a housing 20. It is equipped with The refrigerant circuit 10, the blower 6, and the drain pan 7 are arranged within the housing 20. The casing 20 faces the external space (indoor space) that is targeted for dehumidification by the dehumidifier 1 .

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

Compressor 2 is configured to compress refrigerant. Specifically, the compressor 2 is configured to suck in low-pressure refrigerant from an inlet, compress it, and discharge it as high-pressure refrigerant from a discharge port. The compressor 2 may be configured to have a variable refrigerant discharge capacity. Specifically, the compressor 2 may be an inverter compressor. When the compressor 2 is configured to have a variable refrigerant discharge capacity, the amount of refrigerant circulated within the dehumidifier 1 can be controlled by adjusting the discharge capacity of the compressor 2.

The condenser 3 is configured to condense and cool the refrigerant pressurized by the compressor 2. The condenser 3 is a heat exchanger that exchanges heat between refrigerant and air. The condenser 3 has a refrigerant inlet and an outlet, and an air inlet and an outlet. A refrigerant inlet of the condenser 3 is connected to a discharge port of the compressor 2 via piping.

The condenser 3 includes a first condensing section 3a and a second condensing section 3b. The first condensing section 3a is connected to the second condensing section 3b. The second condensing section 3b is configured to condense and cool the refrigerant pressurized by the compressor 2. The second condensing section 3b is a heat exchanger that exchanges heat between the refrigerant and air. The second condensing section 3b has a refrigerant inlet and an outlet, and an air inlet and an outlet. In this embodiment, the refrigerant inlet of the second condensing section 3b is connected to the discharge port of the compressor 2 via piping. The second condensing section 3b is arranged downstream of the first condensing section 3a in the flow of air generated by the blower 6. In other words, the second condensing section 3b is arranged on the leeward side of the first condensing section 3a. The heat exchanger tube of the second condensing section 3b is a flat tube.

The first condensing section 3a is configured to further condense and cool the refrigerant cooled in the second condensing section 3b. The first condensing section 3a is a heat exchanger that exchanges heat between refrigerant and air. The first condensing section 3a has a refrigerant inlet and an outlet, and an air inlet and an outlet. In this embodiment, the refrigerant inlet of the first condensing section 3a is connected to the outlet of the second condensing section 3b by piping. The first condensing section 3a is arranged upstream of the second condensing section 3b in the flow of air generated by the blower 6. That is, the first condensing section 3a is arranged upwind of the second condensing section 3b. Further, the first condensing section 3a is arranged downstream of the evaporator 5 in the flow of air generated by the blower 6. That is, the first condensing section 3a is disposed downstream of the evaporator 5. The heat exchanger tube of the first condensing section 3a is a circular tube.

The pressure reducing device 4 is configured to reduce the pressure of the refrigerant cooled in the condenser 3 and expand it. The pressure reducing device 4 is, for example, an expansion valve. This expansion valve may be an electronically controlled valve. Note that the pressure reducing device 4 is not limited to an expansion valve, and may be a capillary tube. The pressure reducing device 4 is connected to a refrigerant outlet of the condenser 3 and a refrigerant inlet of the evaporator 5 through piping, respectively.

The evaporator 5 is configured to absorb heat from the refrigerant that has been depressurized and expanded by the pressure reducing device 4 and evaporate the refrigerant. The evaporator 5 is a heat exchanger that exchanges heat between refrigerant and air. The evaporator 5 has a refrigerant inlet and an outlet, and an air inlet and an outlet. The refrigerant outlet of the evaporator 5 is connected to the suction port of the compressor 2 via piping. 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 placed upwind of the condenser 3. Specifically, the evaporator 5 is arranged upwind of the first condensing section 3a. The heat transfer tube of the evaporator 5 is a circular tube.

In this embodiment, the refrigerant circuit 10 is configured to circulate refrigerant in the order of the compressor 2, the second condensing section 3b, the first condensing section 3a, the pressure reducing device 4, and the evaporator 5.

The blower 6 is configured to blow air. The blower 6 is configured to take air into the housing 20 from outside and blow it to the condenser 3 and the evaporator 5. Specifically, the blower 6 takes air into the housing 20 from the outside space (indoor space), passes it through the evaporator 5, the first condensing part 3a, and the second condensing part 3b, and then sends it outside the housing 20. It is configured to exhale.

In this embodiment, the blower 6 has a shaft 6a and a fan 6b that rotates around the shaft 6a. As the fan 6b rotates around the shaft 6a, air taken in from the outside space (indoor space) as shown by arrow A in the figure is transferred to the evaporator 5 and the first condensing section as shown by arrow B in the figure. 3a and the second condensing section 3b, it is again discharged into the external space (indoor space) as shown by arrow C in the figure. In this way, air circulates in the external space (indoor space) via the dehumidifier 1.

The casing 20 includes an inlet 21 for introducing air into the casing 20 from the external space (indoor space) to be dehumidified, and a suction port 21 for blowing air from the inside of the casing 20 into the external space (indoor space). A blower outlet 22 is provided. Furthermore, the housing 20 has an air path (air flow path) 23 that connects the inlet 21 and the outlet 22 . An evaporator 5, a condenser 3, and a blower 6 are arranged in the air passage 23. Therefore, the evaporator 5 and the condenser 3 are arranged in the same air path 23. The evaporator 5, the first condensing section 3a, and the second condensing section 3b are arranged in the air passage 23 in the order of the evaporator 5, the first condensing section 3a, and the second condensing section 3b from upstream to downstream in the air flow. has been done.

In the air passage 23, air sucked into the housing 20 from the outside of the housing 20 through the suction port 21 passes through the evaporator 5, the first condensing part 3a, and the second condensing part 3b in this order, and is blown out. It is blown out of the housing 20 through the outlet 22.

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

Note that when the air conditioner is installed indoors, the indoor space may be cooled by radiating the heat of the condenser 3 to the outdoors. In order to dissipate heat to the outside, the exhaust duct may be mounted on the device and the device itself may be installed near the window.

The drain pan 7 is configured so that dehumidified water condensed on the evaporator 5 or dehumidified water scattered from the evaporator 5 is drained into the drain pan 7. In this embodiment, the evaporator 5, the first condensing section 3a, and the second condensing section 3b are arranged on the drain pan 7.

Next, the configurations of the evaporator 5, the first condensing section 3a, and the second condensing section 3b will be described in detail with reference to FIGS. 3 to 5. FIG. 3 is a cross-sectional view of the evaporator 5, the first condensing section 3a, and the second condensing section 3b according to the first embodiment. In addition, in FIG. 3, for convenience of explanation, a part of the evaporator 5, the first condensing part 3a, and the second condensing part 3b is illustrated.

In the dehumidifying device 1 according to the present embodiment, the first condensing section 3a includes a plurality of first fins 11 and a first heat exchanger tube 12. Each of the plurality of first fins 11 is formed into a thin plate shape. The plurality of first fins 11 are arranged so as to be stacked on each other. The first heat exchanger tubes 12 are arranged so as to pass through the plurality of first fins 11 stacked on each other in the stacking direction. The first heat exchanger tube 12 has a plurality of first straight sections extending linearly in the stacking direction and a plurality of first curved sections connecting the first straight sections. The first heat exchanger tube 12 is configured to meander by connecting each of the plurality of first straight portions and each of the plurality of first curved portions in series. The first heat exchanger tube 12 is configured to allow refrigerant to flow therethrough. The first heat exchanger tube 12 is a circular tube.

The second condensing section 3b includes a plurality of second fins 13 and second heat exchanger tubes 14. Each of the plurality of second fins 13 is formed into a thin plate shape. The plurality of second fins 13 are arranged so as to be stacked on each other. The second heat exchanger tube 14 is arranged so as to pass through the plurality of second fins 13 stacked on each other in the stacking direction. The cross-sectional shape of the second heat exchanger tubes 14 is configured to extend in the column direction. Further, the second heat exchanger tube 14 has a plurality of second linear portions that extend linearly in the stacking direction of the plurality of second fins 13 . Further, the second condensing section 3b includes a first header 31 and a second header 32 that respectively connect the ends of the plurality of second straight sections (see FIG. 4). Each of the plurality of second straight portions of the second heat exchanger tube 14 has a plurality of small-diameter pipe lines. The second heat exchanger tube 14 is configured to allow refrigerant to flow therethrough. The second heat exchanger tube 14 is a flat tube. The second heat transfer tube 14 is a flat tube having a flat shape with respect to the direction of air flow passing through the air passage 23 . The cross-sectional shape of the second heat exchanger tube 14 is configured to have a flat shape extending in the direction in which the first condensing section 3a and the second condensing section 3b are lined up.

Evaporator 5 has a plurality of fins 15 and heat transfer tubes 16. Each of the plurality of fins 15 is formed into a thin plate shape. The plurality of fins 15 are arranged so as to be stacked on each other. The heat exchanger tubes 16 are arranged so as to pass through the plurality of fins 15 stacked on each other in the stacking direction. The heat exchanger tube 16 has a plurality of straight portions extending linearly in the stacking direction and a plurality of curved portions connecting the plurality of straight portions. Each of the plurality of straight portions and each of the plurality of straight portions are connected in series, so that the heat exchanger tube 16 is configured to meander. The heat exchanger tube 16 is a circular tube.

FIG. 3 shows a cross section perpendicular to the stacking direction of the plurality of first fins 11 of the first condensing section 3a, the plurality of second fins 13 of the second condensing section 3b, and the stacking direction of the plurality of fins 15 of the evaporator 5. FIG. In the first condensing section 3a, the first straight portions of the plurality of first heat exchanger tubes 12 are arranged in the cross section shown in FIG. The outer diameter and inner diameter of the first straight portions of the plurality of first heat exchanger tubes 12 may be the same.

In this embodiment, the first straight portions of the plurality of first heat exchanger tubes 12 are arranged in two rows in the column direction. The intervals between the first straight portions of the first heat exchanger tubes 12 arranged in each row in the column direction of these two rows may be the same. Note that this interval is the distance between the centers of the first straight portions of the first heat exchanger tubes 12 arranged in each adjacent row in the row direction. In this embodiment, the first straight portions of the plurality of first heat exchanger tubes 12 in each row adjacent to each other in the row direction are arranged so as to be shifted from each other in the row direction. That is, the centers of the first straight portions of the plurality of first heat exchanger tubes 12 in each row adjacent to each other in the row direction are not arranged in a straight line in the row direction.

Moreover, in this embodiment, the first straight portions of the plurality of first heat exchanger tubes 12 in each row adjacent to each other in the row direction are arranged so as not to overlap with each other in the row direction. Furthermore, in this embodiment, the first straight portions of the plurality of first heat exchanger tubes 12 in each row adjacent to each other in the row direction are arranged so as not to overlap with each other in the row direction.

In this embodiment, the first straight portions of the plurality of first heat exchanger tubes 12 are arranged in three or more stages in the row direction in each row. Further, in this embodiment, the first straight portions of the plurality of first heat exchanger tubes 12 are arranged linearly in the step direction in each row. That is, the centers of the first straight portions of the plurality of first heat exchanger tubes 12 arranged in line in the step direction in each row are arranged in a straight line. Furthermore, in the present embodiment, the position in the column direction of the first straight portion of the plurality of first heat exchanger tubes 12 arranged in each row in the column direction of these two rows is the same as that of the plurality of first heat transfer tubes 12 arranged in each row. It is arranged at the center between the positions of the first straight section in the first heat exchanger tube 12 in the step direction.

In the second condensing section 3b, the second straight portions of the plurality of second heat exchanger tubes 14 are arranged in the cross section shown in FIG. The shapes of the second straight portions in the plurality of second heat exchanger tubes 14 may be the same.

In this embodiment, the second straight portions of the plurality of second heat exchanger tubes 14 are arranged in three or more stages in the stage direction. Further, in this embodiment, the second straight portions of the plurality of second heat exchanger tubes 14 are arranged linearly in the step direction. That is, the centers of the second straight portions of the plurality of second heat exchanger tubes 14 arranged in line in the step direction are arranged in a straight line. Further, the intervals between the second straight portions in the second heat exchanger tubes 14 at each stage may be the same.

FIG. 4 is a front view of the second condensing section 3b when the second condensing section 3b is viewed from the row direction. The flat tube of the second condensing section 3b may be arranged horizontally or vertically. The shape of the second fins 13 of the second condensing section 3b may be plate fins, corrugated fins, or the like. The shape of the second fins 13 of the second condensing section 3b is selected depending on the performance of the second condensing section 3b and the installation posture of the flat tube of the second condensing section 3b. The second heat exchanger tube 14 of the second condensing section 3b includes at least one refrigerant path. In this embodiment, the number of refrigerant paths gradually decreases from upstream to downstream of the refrigerant flow.

Referring to FIGS. 2 and 4, the first header 31 has a refrigerant inlet and a refrigerant outlet. In this embodiment, the refrigerant inlet of the first header 31 is connected to the discharge port of the compressor 2 via piping. Further, the refrigerant outlet of the first header 31 is connected to the inlet of the first condensing section 3a by piping. By providing the partition 33 in the first header 31 and the second header 32, the refrigerant flowing from the compressor 2 passes through the plurality of second straight parts and turns back multiple times between the first header 31 and the second header 32. Thereafter, the refrigerant flows out from the refrigerant outlet of the first header 31 to the first condensing section 3a. At this time, it is preferable that the number of refrigerant paths in the second straight section that reciprocates between the first header 31 and the second header 32 is gradually decreased from the upstream side to the downstream side of the second condensing section 3b. For example, if the number of refrigerant paths on the outward path from the first header 31 to the second header 32 is five, the number of refrigerant paths on the return path from the second header 32 to the first header 31 is preferably four or less.

Moreover, as shown in FIG. 5, the first header 31 and the second header 32 may be divided. As a result, the refrigerant flowing from the compressor 2 passes through the plurality of second straight sections and turns back between the first header 31 and the second header 32 several times, and then is condensed from the refrigerant outlet of the second condensing section 3b. It may flow out to the part 3a. The first header 31 includes a first header upstream portion 311 and a first header downstream portion 312 that are separated from each other. The second header 32 includes a second header upstream portion 321 and a second header downstream portion 322 that are separated from each other. Further, the refrigerant outlet of the second condensing section 3b may be located not in the first header 31 but in the second header 32. In that case, the pipe connecting the first condensing part 3a and the second condensing part 3b is located on the opposite side of the second condensing part 3b from the pipe connecting the compressor 2 and the second condensing part 3b. Become.

In the evaporator 5, the straight portions of the plurality of heat transfer tubes 16 are arranged in the cross section shown in FIG. The outer diameter and inner diameter of the straight portions of these plurality of heat exchanger tubes 16 may be the same.

In this embodiment, the straight portions of the plurality of heat exchanger tubes 16 are arranged in three rows in the column direction. The intervals between the straight portions of the heat exchanger tubes 16 arranged in each of these three rows in the column direction may be the same. Note that this interval is the distance between the centers of straight portions of the heat exchanger tubes 16 arranged in adjacent rows in the row direction. In this embodiment, the straight portions of the plurality of heat exchanger tubes 16 in each row adjacent to each other in the row direction are arranged so as to be shifted from each other in the row direction. That is, the centers of the second straight portions of the plurality of heat exchanger tubes 16 in each row adjacent to each other in the row direction are not arranged in a straight line in the row direction.

Moreover, in this embodiment, the straight portions of the plurality of heat exchanger tubes 16 in each row adjacent to each other in the row direction are arranged so as not to overlap with each other in the row direction. Furthermore, in this embodiment, the straight portions of the plurality of heat transfer tubes 16 in each row adjacent to each other in the row direction are arranged so as not to partially overlap with each other in the row direction.

In the present embodiment, the straight portions of the plurality of heat exchanger tubes 16 are arranged in three or more stages in the row direction in each row. Further, in this embodiment, the straight portions of the plurality of heat exchanger tubes 16 are arranged linearly in the step direction in each row. In other words, the centers of the linear portions of the plurality of heat exchanger tubes 16 arranged in the row direction in each row are arranged in a straight line. Furthermore, in the present embodiment, the positions of the straight portions in the row direction of the plurality of heat exchanger tubes 16 arranged in each of the rows at both ends in the row direction of these three rows are the same. Further, the position in the row direction of the straight portion of the heat exchanger tubes 16 arranged in the center row in the row direction of these three rows is the same as the row direction position of the straight portion of the plurality of heat exchanger tubes 16 arranged in each row at both ends. Centered between positions.

Note that the evaporator 5 and the first condensing section 3a may be a multi-pass type heat exchanger having a plurality of refrigerant paths.

Next, with reference to FIGS. 1 and 2, the operation of the dehumidifying device 1 according to the first embodiment during dehumidifying operation will be described.

The refrigerant in a superheated gas state discharged from the compressor 2 flows into the second condensing section 3b arranged in the air path 23. The refrigerant in a superheated gas state that has flowed into the second condensing section 3b flows into the air passage 23 from the external space through the suction port 21, and passes through the evaporator 5 disposed within the air passage 23 and the first condensing section 3a. It is cooled by exchanging heat with air and becomes a gas-liquid two-phase refrigerant.

On the other hand, the air passing through the second condensing part 3b arranged in the air passage 23 passes through the evaporator 5 and the first condensing part 3a, which are also arranged in the air passage 23, and then enters the second condensing part 3b. It is heated by exchanging heat with a refrigerant in a superheated gas state or a gas-liquid two-phase refrigerant.

The gas-liquid two-phase refrigerant flowing out from the second condensing section 3b flows into the first condensing section 3a. The gas-liquid two-phase refrigerant that has flowed into the first condensing section 3a is further cooled by heat exchange with the air that has passed through the evaporator 5 disposed in the air passage 23, and becomes a supercooled liquid refrigerant. Become.

On the other hand, the air passing through the first condensing part 3a arranged in the air passage 23 passes through the evaporator 5 also arranged in the first air passage 23a, and then enters the first condensing part 3a into a gas-liquid two-phase state. It is heated by exchanging heat with the refrigerant in the state.

The refrigerant in a supercooled liquid state flowing out from the first condensing section 3 a is depressurized by passing through a pressure reducing device 4 and becomes a gas-liquid two-phase refrigerant. flows into. 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 external space through the suction port 21, and becomes a refrigerant in a superheated gas state. This superheated gas refrigerant is sucked into the compressor 2, compressed by the compressor 2, and discharged again.

On the other hand, air passing through the evaporator 5 arranged in the air passage 23 is taken into the air passage 23 from the outside space through the suction port 21, and then heat exchanged with the refrigerant in a gas-liquid two-phase state in the evaporator 5. The air is dehumidified by being cooled to a temperature below the dew point of the air.

Next, the effects of the dehumidifying device 1 according to the first embodiment will be explained in comparison with a comparative example.
FIG. 6 is a cross-sectional view of the evaporator 5 and condenser 3 of the dehumidification device 1 according to a comparative example. Generally, in order to improve the performance of the condenser 3, it is necessary to increase the heat transfer area. In order to increase the heat transfer area, it is necessary to increase the size of the condenser 3. Therefore, in the dehumidifying device 1 according to the comparative example, it is not possible to reduce the size of the condenser 3 while improving its performance. Furthermore, in the dehumidifying device 1 according to the comparative example, the casing 20 becomes larger as the size of the condenser 3 becomes larger. Therefore, in the dehumidifying device 1 according to the comparative example, the housing 20 cannot be downsized either.

According to the dehumidifier 1 according to the present embodiment, the first heat exchanger tube 12 of the first condensing section 3a is a circular tube. Therefore, it is possible to suppress the dehumidified water splashed from the evaporator 5 to the first condensing section 3a from staying in the first heat exchanger tube 12. Thereby, the drainage performance of the first condensing section 3a can be improved. Therefore, it is possible to prevent the air from being re-humidified due to the dehumidified water retained in the first heat exchanger tube 12 of the first condensing section 3a being heated and evaporated by the refrigerant. Therefore, the amount of dehumidification of the dehumidifier 1 can be improved. Further, the second heat exchanger tube 14 of the second condensing section 3b is a flat tube. Thereby, the heat transfer performance of the second condensing section 3b can be improved. Furthermore, the length of the second condensing section 3b in the column direction can be shortened compared to the case where a circular tube having heat transfer performance equivalent to that of a flat tube is used for the second condensing section 3b. Therefore, the size of the condenser 3 can be reduced while improving its performance, and the amount of dehumidification can be improved.

Further, by shortening the length of the second condensing section 3b in the column direction, the size of the condenser 3 can be reduced. Therefore, by reducing the size of the condenser 3, the casing 20 of the dehumidifier 1 can also be reduced in size.

Further, since the second heat transfer tube 14 of the second condensing section 3b is a flat tube with excellent heat transfer performance, the condensing temperature in the first condensing section 3a and the second condensing section 3b can be lowered. Moreover, since the difference between the condensation pressure and the evaporation pressure in the refrigerant circuit can be reduced by lowering the condensing temperature, the input to the compressor 2 can be lowered. Thereby, it is possible to improve the EF (Energy Factor) value (L/KWh), which indicates the amount of dehumidification L per 1 kWh, which is an index indicating the dehumidification performance of the dehumidifier 1.

Further, the second heat exchanger tube 14 of the second condensing section 3b is a flat tube having a flat shape with respect to the flow direction of the air passing through the air passage 23. Therefore, ventilation resistance can be reduced compared to a circular pipe. By reducing the ventilation resistance, the fan input to the blower 6 can be reduced. Therefore, the EF value can be improved.

Moreover, since the first condensing section 3a has plate fins and circular heat exchanger tubes, it is possible to suppress the dehumidified water from scattering to the second condensing section 3b having flat heat exchanger tubes. In addition, in the first condensing section 3a, which is a combination of plate fins and a circular pipe, dehumidified water is drained from both sides of the circular pipe in the radial direction to the drain pan 7 along the plate fins, so it has better drainage performance than a flat pipe. There is. Therefore, it is possible to suppress a decrease in heat exchange performance due to accumulation of dehumidified water and a decrease in dehumidification amount due to heating of dehumidified water.

Moreover, according to the dehumidifier 1 according to the present embodiment, in the second condensing section 3b, the number of refrigerant paths gradually decreases from upstream to downstream of the flow of the refrigerant. That is, in the second condensing section 3b, the number of refrigerant paths in the second straight section that reciprocates between the first header 31 and the second header 32 gradually decreases from the upstream side to the downstream side. Since the refrigerant in the gas state on the upstream side has a larger pressure loss than the refrigerant in the gas-liquid two-phase state, the pressure loss can be reduced by increasing the number of refrigerant passes and reducing the flow velocity for the refrigerant in the gas state on the upstream side. can be reduced. In addition, since the refrigerant in the gas-liquid two-phase state on the downstream side has a smaller pressure loss than the refrigerant in the gas state, the flow rate can be increased by reducing the number of refrigerant passes for the refrigerant in the two-phase gas-liquid state on the downstream side. By doing so, the heat transfer coefficient can be improved.

Embodiment 2.
A dehumidifying device 1 according to a second embodiment will be described with reference to FIGS. 7 and 8. The dehumidifier 1 according to the present embodiment is configured such that the refrigerant circuit 10 circulates refrigerant in the order of the compressor 2, the first condensing section 3a, the second condensing section 3b, the pressure reducing device 4, and the evaporator 5. This is different from the dehumidifying device 1 of the first embodiment in that the dehumidifying device 1 is different from the dehumidifying device 1 of the first embodiment.

In the dehumidifier 1 according to the present embodiment, the refrigerant inlet of the first condensing section 3a is connected to the discharge port of the compressor 2 via piping. A refrigerant outlet of the first condensing section 3a is connected to a refrigerant inlet of the second condensing section 3b via piping. The refrigerant outlet of the second condensing section 3b is connected to the pressure reducing device 4 via piping.

According to the dehumidifier 1 according to the present embodiment, the refrigerant circuit 10 is configured to circulate refrigerant in the order of the compressor 2, the first condensing section 3a, the second condensing section 3b, the pressure reducing device 4, and the evaporator 5. has been done. Since the flat tube has a small diameter, the pressure loss is larger than that of the circular tube. Further, the pressure loss of the refrigerant in the gas state is greater than the pressure loss of the refrigerant in the liquid state. Therefore, by allowing the refrigerant in a superheated gas state to flow into the circular pipe of the first condensing part 3a before the flat pipe of the second condensing part 3b, the refrigerant can enter the second condensing part 3b in a gas-liquid two-phase state or in a supercooled liquid state. refrigerant can be flowed in. Therefore, pressure loss in the second condensing section 3b can be reduced. Furthermore, since the gas-liquid two-phase or liquid refrigerant flows into the flat tube, which has a smaller internal volume than the circular tube, the amount of refrigerant can be reduced.

Embodiment 3.
A dehumidifying device 1 according to a third embodiment will be described with reference to FIGS. 9 to 11. The dehumidifier 1 according to the present embodiment has a third condensing part 3c, a first suction port 21a, a second suction port 21b, a partition part 8, a first air path 23a, and a second air path 23b. , which is different from the dehumidifying device 1 of the first embodiment.

Referring to FIGS. 9 and 10, in the dehumidifier 1 according to the present embodiment, the housing 20 includes a first suction port 21a, a second suction port 21b, a first air path 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 separated from the first air passage 23a.

The condenser 3 includes a third condensing section 3c. The third condensing section 3c is arranged between the compressor 2 and the second condensing section 3b in the refrigerant circuit 10. The refrigerant circuit 10 is configured to circulate refrigerant in the order of the compressor 2, the third condensing section 3c, the second condensing section 3b, the first condensing section 3a, the pressure reducing device 4, and the evaporator 5.

Referring to FIGS. 10 and 11, the third condensing section 3c is configured to condense and cool the refrigerant pressurized by the compressor 2. The third condensing section 3c is a heat exchanger that exchanges heat between the refrigerant and air. The third condensing section 3c has a plurality of third fins 17 and third heat exchanger tubes 18. The third condensing section 3c has a refrigerant inlet and an outlet, and an air inlet and an outlet. The refrigerant inlet and outlet of the third condensing section 3c are connected to the discharge port of the compressor 2 and the refrigerant inlet of the second condensing section 3b, respectively, by piping. The third heat exchanger tube 18 is a flat tube.

In this embodiment, the third condensing section 3c is a flat tube heat exchanger having fins and heat transfer tubes having the same shape as the second condensing section 3b. The third condensing section 3c is located above the second condensing section 3b in the stage direction. That is, the linear portion of the third heat exchanger tube 18 of the third condensing section 3c is arranged in line with the second heat exchanger tube 14 of the second condensing section 3b in the step direction. Note that the third heat exchanger tube 18 is not limited to a flat tube, but may be a circular tube.

The first suction port 21a and the second suction port 21b are provided to introduce air into the housing 20 from the external space (indoor space). The first air passage 23a is configured to connect the first suction port 21a and the air outlet 22. An evaporator 5, a first condensing section 3a, a second condensing section 3b, and a blower 6 are arranged in the first air passage 23a. The evaporator 5, the first condensing part 3a, and the second condensing part 3b are connected to the first condensing part 3b so that the air taken in from the first suction port 21a flows in the order of the evaporator 5, the first condensing part 3a, and the second condensing part 3b. It is arranged within the air passage 23a. The second air passage 23b is configured to connect the second suction port 21b and the blowout port 22. A third condensing section 3c and a blower 6 are arranged in the second air passage 23b. The third condensing part 3c is arranged in the second air passage 23b so that the air taken in from the second suction port 21b flows.

In this embodiment, as the fan 6b rotates around the shaft 6a, air taken in from the external space (indoor space) as shown by the arrow A in the figure is drawn into the first air path 23a as shown in the figure. As shown by arrow B, it passes through the evaporator 5, the first condensing section 3a, and the second condensing section 3b. Furthermore, as the fan 6b rotates around the shaft 6a, the air taken in from the external space (indoor space) as shown by the arrow A' in the figure is transferred to the second air passage 23b as shown by the arrow B' in the figure. As shown, it passes through the third condensing section 3c. 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 are discharged through the air outlet 22 into the external space (indoor space) of the housing 20.

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 in the second air passage 23b, one end of the partition portion 8 located on the upstream side is formed at least on the upstream side of the air outlet of the evaporator 5. In the above-mentioned flow direction, the other end of the partition section 8 located on the downstream side is formed at least on the downstream side of the air inlet of the first condensing section 3a. The partition portion 8 is formed, for example, in a flat plate shape. The partition part 8 is fixed inside the housing 20.

According to the dehumidifier 1 according to the present embodiment, the air taken in from the first suction port 21a is transferred to the evaporator 5, the first condensing section 3a, and the second condensing section 3b. , the second condensing section 3b, and the second condensing section 3b. The third condensing part 3c is arranged in the second air passage 23b so that the air taken in from the second suction port 21b flows. Therefore, the amount of air flowing through the entire condenser 3 including the first condensing section 3a, second condensing section 3b, and third condensing section 3c can be made larger than the amount of 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. Moreover, since the difference between the condensation pressure and the evaporation pressure in the refrigerant circuit can be reduced by lowering the condensing temperature, the input to the compressor 2 can be reduced. Thereby, the EF value can be improved.

Further, the third heat exchanger tube 18 of the third condensing section 3c may be a circular tube. By making the third heat transfer tube 18 of the third condensing section 3c a circular tube with small pressure loss, pressure loss due to superheated gas can be reduced. In addition, since the refrigerant in a gas-liquid two-phase state can flow into the second condensing section 3b, which is a flat tube whose internal volume is smaller than that of a circular tube, the amount of refrigerant can be reduced.

Further, the material constituting the partition portion 8 may be made of a material having a lower thermal conductivity than the material constituting the heat transfer tubes and fins through which the refrigerant flows in the evaporator 5 and the first condensing portion 3a. 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.

Embodiment 4.
With reference to FIG. 12, a dehumidifying device 1 according to Embodiment 4 will be described. The dehumidifier 1 according to the present embodiment differs from the dehumidifier 1 according to the third embodiment in that the second condensing section 3b and the third condensing section 3c are integrated.

In the dehumidifying device 1 according to the present embodiment, the second condensing section 3b and the third condensing section 3c are integrally configured. Specifically, each of the plurality of second fins 13 and each of the plurality of third fins 17 are each integrally configured.

According to the dehumidifier 1 according to the present embodiment, the heat transfer area of the second condensing section 3b and the third condensing section 3c is larger than the heat transfer area of the first condensing section 3a. Furthermore, of the second condensing section 3b and the third condensing section 3c that are integrally configured, the second condensing section 3b exchanges heat with the air passing through the first air path 23a. Of the second condensing section 3b and the third condensing section 3c that are integrally configured, the third condensing section 3c exchanges heat with the air passing through the second air path 23b. As a result, the same effects as in the third embodiment can be obtained.

Moreover, according to the dehumidifier 1 according to the present embodiment, the second condensing section 3b and the third condensing section 3c are integrally configured. Therefore, the cost of the header and connecting piping can be reduced.

The above embodiments can be combined as appropriate.
The embodiments disclosed this time should be considered to be illustrative in all respects and not restrictive. The scope of the present disclosure is indicated by the claims rather than the above description, and it is intended that all changes within the meaning and range equivalent to the claims are included.

1 dehumidifier, 2 compressor, 3 condenser, 3a first condensing section, 3b second condensing section, 3c third condensing section, 4 pressure reducing device, 5 evaporator, 6 blower, 7 drain pan, 8 partition, 10 refrigerant circuit, 11 first fin, 12 first heat exchanger tube, 13 second fin, 14 second heat exchanger tube, 15 fin, 16 heat exchanger tube, 17 third fin, 18 third heat exchanger tube, 20 housing, 21 suction port, 21a first inlet, 21b second inlet, 22 outlet, 23 air passage, 23a first air passage, 23b second air passage, 31 first header, 32 second header.

Claims (5)

A casing and
comprising a blower and a refrigerant circuit arranged in the housing,
The blower is configured to blow air,
The refrigerant circuit includes a compressor, a condenser, a pressure reducing device, and an evaporator, and is configured to circulate the refrigerant in the order of the compressor, the condenser, the pressure reducing device, and the evaporator,
The condenser includes a first condensing section having a first heat exchanger tube through which the refrigerant flows, and a second condensing section having a second heat exchanger tube through which the refrigerant flows,
The first condensing section is located downstream of the evaporator,
The second condensing section is located downstream of the first condensing section,
The first heat exchanger tube of the first condensing section is a circular tube,
In the dehumidification device, the second heat exchanger tube of the second condensing section is a flat tube. The second heat exchanger tube of the second condensing section includes at least one refrigerant path,
The dehumidification device according to claim 1, wherein the number of the refrigerant paths gradually decreases from upstream to downstream of the flow of the refrigerant. The dehumidifier according to claim 1 or 2, wherein the refrigerant circuit is configured to circulate the refrigerant in the order of the compressor, the first condensing section, the second condensing section, the pressure reducing device, and the evaporator. Device. The casing includes 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 first air passage communicating with the second suction port. and a second air path separated from the first air path,
The condenser includes a third condensing section disposed between the compressor and the second condensing section in the refrigerant circuit,
The evaporator, the first condensing section, and the second condensing section are configured such that the air taken in from the first suction port flows through the evaporator, the first condensing section, and the second condensing section in this order. It is located in the first wind path,
The dehumidifier according to any one of claims 1 to 3, wherein the third condensing section is arranged in the second air path so that the air taken in from the second suction port flows therethrough. The dehumidification device according to claim 4, wherein the second condensation section and the third condensation section are integrally configured.

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