Dehumidifying device

Abstract

The dehumidification device includes a housing, a blower, and a refrigerant circuit. The blower and refrigerant circuit are housed within the housing. The blower mechanism supplies air. The refrigerant circuit includes a compressor, a condenser (3), a pressure reducing device, and an evaporator (5), and is configured to circulate the refrigerant in the order of compressor, condenser (3), pressure reducing device, and evaporator (5). The condenser (3) has a first heat transfer tube (12) for refrigerant flow. The evaporator (5) has a second heat transfer tube (14) for refrigerant flow. The condenser (3) is positioned on the downwind side of the evaporator (5). The first heat transfer tube (12) of the condenser (3) is a flat tube and extends horizontally. The second heat transfer tube (14) of the evaporator (5) is a flat tube and extends vertically.

Description

Technical Field

[0001] This disclosure relates to dehumidification devices. Background Technology

[0002] Previously, dehumidification devices using flat tubes in heat transfer tubes to improve the performance of heat exchangers have been proposed. For example, International Patent Publication No. 2019 / 077744 (Patent Document 1) describes a dehumidification device using flat tubes in the heat transfer tubes of a condenser. In the dehumidification device described in that document, round tubes are used in the heat transfer tubes of the evaporator.

[0003] Existing technical documents

[0004] Patent documents

[0005] Patent Document 1: International Publication No. 2019 / 077744 Summary of the Invention

[0006] The problem the invention aims to solve

[0007] In the aforementioned literature, the use of circular tubes in the heat transfer tubes of the evaporator makes it difficult to improve the performance of the evaporator.

[0008] In dehumidification devices, dehumidified water condenses on the surface of the evaporator. If the flat tubes described in the aforementioned literature are used as heat transfer tubes in the evaporator, the poor drainage of the flat tubes will cause dehumidified water to remain on their surface. This retained dehumidified water hinders heat exchange between the refrigerant and the air within the flat tubes, thus reducing the evaporator's heat transfer performance. Consequently, the dehumidification capacity of the dehumidification device is reduced.

[0009] This disclosure was made in view of the above-mentioned issues, and its purpose is to provide a dehumidification device that can improve the performance of the evaporator and increase the dehumidification capacity.

[0010] means for solving problems

[0011] The dehumidification device disclosed herein includes a housing, a blower, and a refrigerant circuit. The blower and refrigerant circuit are disposed within the housing. The blower mechanism supplies 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 compressor, condenser, pressure reducing device, and evaporator. The condenser has a first heat transfer tube for refrigerant flow. The evaporator has a second heat transfer tube for refrigerant flow. The condenser is positioned downwind of the evaporator. The first heat transfer tube of the condenser is a flat tube and extends horizontally. The second heat transfer tube of the evaporator is a flat tube and extends vertically.

[0012] The effects of the invention

[0013] According to the dehumidification device disclosed herein, the second heat transfer tube of the evaporator is a flat tube and extends in the vertical direction. Therefore, the performance of the evaporator can be improved, and the dehumidification capacity can be increased. Attached Figure Description

[0014] Figure 1 This is the refrigerant circuit diagram of the dehumidification device in Embodiment 1.

[0015] Figure 2 This is a schematic diagram showing the structure of the dehumidification device according to Embodiment 1.

[0016] Figure 3 This is a cross-sectional view of the evaporator and condenser of the dehumidification device of Embodiment 1, perpendicular to the stacking direction of the multiple fins of the condenser.

[0017] Figure 4 This is a front view of the condenser of the dehumidification device in Embodiment 1.

[0018] Figure 5 This is a front view of a modified example 1 of the condenser of the dehumidification device according to Embodiment 1.

[0019] Figure 6 This is a front view of a modified example 2 of the condenser of the dehumidification device of embodiment 1.

[0020] Figure 7 This is a front view of a modified example 3 of the condenser of the dehumidification device according to Embodiment 1.

[0021] Figure 8 This is a front view of a modified example 4 of the condenser of the dehumidification device in Embodiment 1.

[0022] Figure 9 This is a cross-sectional view of the evaporator and condenser of the dehumidification device of Embodiment 1, perpendicular to the stacking direction of the multiple fins of the evaporator.

[0023] Figure 10 This is a front view of the evaporator of the dehumidification device in Embodiment 1.

[0024] Figure 11 This is a front view of a modified example 1 of the evaporator of the dehumidification device according to Embodiment 1.

[0025] Figure 12 This is a front view of a modified example 2 of the evaporator of the dehumidification device of embodiment 1.

[0026] Figure 13 This is a front view of a modified example 3 of the evaporator of the dehumidification device according to Embodiment 1.

[0027] Figure 14 This is a front view of a modified example 4 of the evaporator of the dehumidification device in Embodiment 1.

[0028] Figure 15 This is a front view of a modified example 5 of the evaporator of the dehumidification device according to Embodiment 1.

[0029] Figure 16 This is a cross-sectional view in the layer direction of a section of the evaporator and condenser of the dehumidification device of Embodiment 1, which is a modified example 5 of the evaporator and the condenser, and is perpendicular to the stacking direction of the plurality of fins of the evaporator.

[0030] Figure 17 This is a cross-sectional view of the evaporator and condenser of the dehumidification device in the comparative example of Embodiment 1.

[0031] Figure 18 This is the refrigerant circuit diagram of the dehumidification device in Embodiment 2.

[0032] Figure 19 This is a schematic diagram showing the structure of the dehumidification device according to Embodiment 2.

[0033] Figure 20 This is a cross-sectional view of the evaporator and condenser of the dehumidification device of Embodiment 2, perpendicular to the stacking direction of the multiple fins of the condenser.

[0034] Figure 21 This is the refrigerant circuit diagram of the dehumidification device in Embodiment 3.

[0035] Figure 22 This is a schematic diagram showing the structure of the dehumidification device according to Embodiment 3.

[0036] Figure 23 This is a cross-sectional view of the evaporator and condenser of the dehumidification device in Embodiment 3, perpendicular to the stacking direction of the multiple fins of the condenser. Detailed Implementation

[0037] The embodiments will now be described with reference to the accompanying drawings. Furthermore, in the drawings, identical or equivalent parts are labeled with the same reference numerals, and their descriptions will not be repeated.

[0038] Implementation method 1.

[0039] Reference Figure 1 and Figure 2 The structure of the dehumidification device 1 in Embodiment 1 will be described. Figure 1 This is the refrigerant circuit diagram of the dehumidification device 1 in Embodiment 1. Figure 2 This is a schematic diagram showing the structure of the dehumidification device 1 according to Embodiment 1.

[0040] like Figure 1 and Figure 2As shown, the dehumidifier 1 includes a refrigerant circuit 101, a blower 6, a drain pan 7, and a housing 20. 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 arranged inside the housing 20. The housing 20 faces the external space (indoor space) to which the dehumidifier 1 is dehumidified.

[0041] The refrigerant circuit 101 is configured to circulate the refrigerant in the order of compressor 2, condenser 3, pressure reducing device 4, and evaporator 5. Specifically, the refrigerant circuit 101 is constructed by connecting the compressor 2, condenser 3, pressure reducing device 4, and evaporator 5 using piping. Furthermore, the refrigerant circulates within this piping, thus circulating in the refrigerant circuit 101 in the order of compressor 2, condenser 3, pressure reducing device 4, and evaporator 5. Figure 2 In the diagram, the solid arrow marking refrigerant circuit 101 indicates the flow of refrigerant in refrigerant circuit 101.

[0042] Compressor 2 is configured to compress refrigerant. Specifically, compressor 2 is configured to draw in low-pressure refrigerant through the suction port, compress it, and discharge it as high-pressure refrigerant through the discharge port. Compressor 2 may also be configured to have a variable refrigerant discharge capacity. Specifically, compressor 2 may also be a variable frequency compressor. When compressor 2 is configured to have a variable refrigerant discharge capacity, the amount of refrigerant circulating in dehumidification device 1 can be controlled by adjusting the discharge capacity of compressor 2.

[0043] The condenser 3 is configured to cool the refrigerant after it has been pressurized by the compressor 2 by condensing it. The condenser 3 is a heat exchanger that facilitates heat exchange between the refrigerant and air. The condenser 3 has a refrigerant inlet and an air inlet and an air outlet. The refrigerant inlet of the condenser 3 is connected to the outlet of the compressor 2 via piping. The condenser 3 is positioned downstream of the evaporator 5 in the airflow generated by the blower 6. That is, the condenser 3 is located on the leeward side compared to the evaporator 5. The heat transfer tubes of the condenser 3 are flat tubes.

[0044] The pressure reducing device 4 is configured to reduce the pressure of the refrigerant after it has been cooled by the condenser 3, causing it to expand. The pressure reducing device 4 is, for example, an expansion valve. This expansion valve can also be an electronically controlled valve. Furthermore, the pressure reducing device 4 is not limited to an expansion valve; it can also be a capillary tube. The pressure reducing device 4 is connected via piping to the refrigerant outlet of the condenser 3 and the refrigerant inlet of the evaporator 5, respectively.

[0045] The evaporator 5 is configured to allow the refrigerant, after being depressurized and expanded by the pressure reducing device 4, to absorb heat, thereby causing the refrigerant to evaporate. The evaporator 5 is a heat exchanger that facilitates heat exchange between the 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 positioned upstream of the condenser 3 in the airflow generated by the blower 6. That is, the evaporator 5 is positioned on the upwind side compared to the condenser 3. The heat transfer tubes of the evaporator 5 are flat tubes.

[0046] The blower 6 is configured to supply air. Moreover, the blower 6 is configured to draw air from the outside of the housing 20 into the interior and supply air to the condenser 3 and the evaporator 5. Specifically, the blower 6 is configured to draw air from the external space (indoor space) into the housing 20 and discharge it to the outside of the housing 20 after passing through the evaporator 5 and the condenser 3.

[0047] In this embodiment, the blower 6 has a shaft 6a and a fan 6b that rotates around the shaft 6a. The fan 6b rotates around the shaft 6a, thereby drawing air from the external space (indoor space) as shown by arrow A in the figure, passing sequentially through the evaporator 5 and the condenser 3 as shown by arrow B in the figure, and then discharging it back into the external space (indoor space) as shown by arrow C in the figure. In this way, the air circulates in the external space (indoor space) via the dehumidifier 1.

[0048] The housing 20 is provided with an intake 21 for allowing air to enter the interior of the housing 20 from the external space (indoor space) to be dehumidified, and an exhaust 22 for blowing air from the interior of the housing 20 to the external space (indoor space). Furthermore, the housing 20 has an airflow path 23 connecting the intake 21 and the exhaust 22. An evaporator 5, a condenser 3, and a blower 6 are arranged in the airflow path 23. Therefore, the evaporator 5 and the condenser 3 are arranged within the same airflow path 23. The evaporator 5 and the condenser 3 are arranged in the airflow path 23 in the order of evaporator 5 and condenser 3, moving from upstream to downstream in the airflow.

[0049] Within the air passage 23, air drawn into the interior of the housing 20 from the outside through the intake port 21 passes through the evaporator 5 and the condenser 3 in sequence, and is blown out to the outside of the housing 20 through the outlet 22.

[0050] In addition, in the dehumidification device 1, components constituting the refrigerant circuit may be arranged in the air duct 23, other than the condenser 3, evaporator 5, and blower 6. For example, a pressure reducing device 4 may also be arranged in the air duct 23.

[0051] Alternatively, if the dehumidifier 1 is installed indoors, the room can be cooled by dissipating heat from the condenser 3 to the outside. To dissipate this heat to the outside, an exhaust pipe can be installed on the device, and the device itself can be positioned near a window.

[0052] The drain pan 7 is configured such that dehumidified water that has condensed at the evaporator 5 is discharged into the drain pan 7. In this embodiment, the evaporator 5 and the condenser 3 are positioned above the drain pan 7.

[0053] Next, refer to Figures 3 to 16 The structure of evaporator 5 and condenser 3 is described in detail. Figure 3 This is a cross-sectional view of the evaporator 5 and condenser 3 of Embodiment 1, perpendicular to the stacking direction of the plurality of fins 11 of the condenser 3. Additionally, in Figure 3 For ease of explanation, a portion of the evaporator 5 and the condenser 3 are shown in the diagram.

[0054] In the dehumidification device 1 of this embodiment, the condenser 3 has a plurality of fins (first fins) 11 and a heat transfer tube (first heat transfer tube) 12. The plurality of fins 11 are each configured as a thin plate. The plurality of fins 11 are arranged in a stacked manner. The heat transfer tube 12 is arranged such that it passes through the stacked fins 11 in the stacking direction. The cross-sectional shape of the heat transfer tube 12 is configured to extend along the column direction. Furthermore, the heat transfer tube 12 has a plurality of straight portions extending linearly in the stacking direction of the plurality of fins 11. In addition, the condenser 3 has a first head 31 and a second head 32 (see reference) that respectively connect the ends of the plurality of straight portions. Figure 4 The heat transfer tube 12 has multiple straight sections, each with a multiple narrow diameter. The heat transfer tube 12 is configured to supply refrigerant flow. The heat transfer tube 12 of the condenser 3 is a flat tube. The heat transfer tube 12 is a flat tube with a flat shape relative to the direction of airflow through the air passage 23. The cross-sectional shape of the heat transfer tube 12 is configured to have a flat shape extending in the direction in which the condenser 3 and the evaporator 5 are arranged.

[0055] Figure 3 A cross-sectional view is shown, perpendicular to the stacking direction of the plurality of fins 11 in the condenser 3. In the condenser 3, in... Figure 3 The cross-section shown includes straight sections of multiple heat transfer tubes 12. The shapes of these straight sections of the multiple heat transfer tubes 12 may also be identical.

[0056] In this embodiment, the straight sections of the plurality of heat transfer tubes 12 are arranged in three or more layers in the layer direction. Furthermore, in this embodiment, the straight sections of the plurality of heat transfer tubes 12 are arranged in a straight line in the layer direction. That is, the centers of the straight sections of the plurality of heat transfer tubes 12 arranged in the layer direction are aligned on a straight line. Moreover, the spacing between the straight sections of the heat transfer tubes 12 in each layer can be the same.

[0057] Figure 4 This is a front view of the condenser 3 as viewed from the column direction. The flat tubes of the condenser 3 extend horizontally. The fins 11 of the condenser 3 are 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 tubes 12 of the condenser 3 contain at least one refrigerant path (first refrigerant path). In this embodiment, the number of refrigerant paths (first refrigerant paths) gradually decreases from upstream to downstream of the refrigerant flow.

[0058] Reference Figure 2 and Figure 4 The first head 31 has a refrigerant inlet and a refrigerant outlet. In this embodiment, the refrigerant inlet of the first head 31 is connected to the discharge port of the compressor 2 via a piping. Furthermore, the refrigerant outlet of the first head 31 is connected to the inlet of the pressure reducing device 4 via a piping. By providing a separator 33 within the first head 31 and the second head 32, the refrigerant flowing in from the compressor 2, after passing through multiple straight sections and repeatedly turning back between the first head 31 and the second head 32, flows out from the refrigerant outlet of the first head 31 to the pressure reducing device 4. At this time, the number of refrigerant paths in the straight sections reciprocating between the first head 31 and the second head 32 preferably gradually decreases from the upstream side of the condenser 3 towards the downstream side. For example, if the number of refrigerant paths from the first head 31 to the second head 32 is 5, then the number of refrigerant paths returning from the second head 32 to the first head 31 is preferably 4 or less.

[0059] Reference Figure 5 The shape of the fins 11 of the condenser 3 can be corrugated fins.

[0060] In addition, such as Figure 6 As shown, the first head 31 and the second head 32 can also be separated. Therefore, the refrigerant flowing in from the compressor 2 can, after passing through multiple straight sections and turning back several times between the first head 31 and the second head 32, flow out from the refrigerant outlet of the condenser 3 to the pressure reducing device 4. The first head 31 includes a first head upstream portion 311 and a first head downstream portion 312, which are separated from each other. The second head 32 includes a second head upstream portion 321 and a second head downstream portion 322, which are separated from each other.

[0061] Furthermore, the refrigerant outlet of the condenser 3 may be located at the second head 32 instead of the first head 31. In this case, the piping connecting the pressure reducing device 4 and the condenser 3 is located on the opposite side of the piping connecting the compressor 2 and the condenser 3, separated by the condenser 3. Alternatively, the separator 33 may not be provided, allowing the refrigerant flowing from the compressor 2 into the first head to flow out through the outlet of the second head 32 to the pressure reducing device 4, without reciprocating between the first head 31 and the second head 32.

[0062] In addition, such as Figure 7 As shown, the heat transfer tube 12 connected to the first head 31 may have multiple straight sections as well as multiple curved sections. After multiple folds between the first head 31 and the second head 32 through multiple straight sections and multiple curved sections, it is connected to the second head 32.

[0063] In addition, such as Figure 8 As shown, the condenser 3 may also have only a first head 31 without a second head 32. In this case, the heat transfer tube 12 has multiple straight sections and multiple curved sections, which fold back multiple times in the horizontal direction from the upstream side of the first head 31 and connect to the downstream side of the first head 31.

[0064] Figure 9 This is a cross-sectional view of the evaporator 5 and condenser 3 of Embodiment 1, perpendicular to the stacking direction of the plurality of fins 13 of the evaporator 5. Additionally, in Figure 9 For ease of explanation, a portion of the evaporator 5 and the condenser 3 are shown in the diagram.

[0065] The evaporator 5 has multiple fins (second fins) 13 and heat transfer tubes (second heat transfer tubes) 14. The multiple fins 13 are each configured as a thin plate. The multiple fins 13 are arranged in a stacked manner. The heat transfer tube 14 is arranged to pass through the stacked multiple fins 13 in the stacking direction. The cross-sectional shape of the heat transfer tube 14 is configured to extend in a column direction. Furthermore, the heat transfer tube 14 has multiple straight portions extending linearly in the stacking direction of the multiple fins 13. In addition, the evaporator 5 has a first head 34 and a second head 35 (see reference) that respectively connect the ends of the multiple straight portions. Figure 10 The heat transfer tube 14 has multiple straight sections, each with a multiple narrow diameter. The heat transfer tube 14 is configured to supply refrigerant flow. The heat transfer tube 14 of the evaporator 5 is a flat tube. The heat transfer tube 14 is a flat tube with a flat shape relative to the direction of airflow in the air passage 23. The cross-sectional shape of the heat transfer tube 14 is configured to have a flat shape extending in the direction in which the condenser 3 and the evaporator 5 are arranged.

[0066] Figure 9 A cross-sectional view is shown, perpendicular to the stacking direction of the plurality of fins 13 in the evaporator 5. In the evaporator 5, in... Figure 9The cross-section shown includes straight sections of multiple heat transfer tubes 14. The straight sections of these heat transfer tubes 14 may also have the same shape.

[0067] In this embodiment, the straight sections of the plurality of heat transfer tubes 14 are arranged in three or more layers in the layer direction. Furthermore, in this embodiment, the straight sections of the plurality of heat transfer tubes 14 are arranged in a straight line in the layer direction. That is, the centers of the straight sections of the plurality of heat transfer tubes 14 arranged in the layer direction are aligned on a straight line. Additionally, the spacing between the straight sections of the heat transfer tubes 14 in each layer can be the same.

[0068] Figure 10 This is a front view of the evaporator 5 as 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 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 tubes 14 of the evaporator 5 contain at least one refrigerant path (second refrigerant path). In this embodiment, the number of refrigerant paths (second refrigerant paths) gradually increases from upstream to downstream of the refrigerant flow.

[0069] Reference Figure 2 and Figure 10 The first head 34 has a refrigerant inlet and a refrigerant outlet. In this embodiment, the refrigerant inlet of the first head 34 is connected to the outlet of the pressure reducing device 4 via a pipe. Furthermore, the refrigerant outlet of the first head 34 is connected to the suction inlet of the compressor 2 via a pipe. By providing a separator 36 within the first head 34 and the second head 35, the refrigerant flowing in from the pressure reducing device 4, after passing through multiple straight sections and repeatedly turning back between the first head 34 and the second head 35, flows out from the refrigerant outlet of the first head 34 to the compressor 2. At this time, the number of refrigerant paths in the straight sections reciprocating between the first head 34 and the second head 35 preferably gradually increases from the upstream side of the evaporator 5 towards the downstream side. For example, if the number of refrigerant paths from the first head 34 to the second head 35 is 5, then the number of refrigerant paths returning from the second head 35 to the first head 34 is preferably 6 or more.

[0070] Furthermore, the positional relationship between the first head 34 and the second head 35 can also be reversed vertically, separated by the heat transfer tube 14. That is, the first head 34 can also be located vertically upwards, separated from the second head 35 by the heat transfer tube 14.

[0071] Reference Figure 11 The fins 13 of the evaporator 5 can also be corrugated fins. Alternatively, the evaporator 5 can also be a finless heat exchanger without fins 13.

[0072] In addition, such as Figure 12As shown, the first head 34 and the second head 35 can also be separated. Therefore, the refrigerant flowing in from the pressure reducing device 4 can flow from the refrigerant outlet of the evaporator 5 to the compressor 2 after passing through multiple straight sections and turning back several times between the first head 34 and the second head 35. The first head 34 includes a first head upstream portion 341 and a first head downstream portion 342, which are separated from each other. The second head 35 includes a second head upstream portion 351 and a second head downstream portion 352, which are separated from each other.

[0073] Furthermore, the refrigerant outlet of the evaporator 5 may be located at the second head 35 instead of the first head 34. In this case, the piping connecting the compressor 2 and the evaporator 5 is located on the opposite side of the piping connecting the compressor 2 and the condenser 3, separated by the condenser 3. Alternatively, the separator 36 may be omitted, allowing the refrigerant flowing from the pressure reducing device 4 into the first head to flow out through the outlet of the second head 35 to the compressor 2, without reciprocating between the first head 34 and the second head 35.

[0074] In addition, such as Figure 13 As shown, the heat transfer tube 14 connected to the first head 34 may have multiple straight sections as well as multiple curved sections, and may be connected to the second head 35 after multiple folds through multiple straight sections and multiple curved sections between the first head 34 and the second head 35.

[0075] In addition, such as Figure 14 As shown, the evaporator 5 may also lack the second head 35 and have only the first head 34. In this case, the heat transfer tube 14 has multiple straight sections and multiple curved sections, which fold back multiple times in the vertical direction from the upstream side of the first head 34 and connect to the downstream side of the first head 34.

[0076] In addition, such as Figure 15 and Figure 16 As shown, the fins 13 of the evaporator 5 can also be configured to extend integrally with the straight portion of the heat transfer tube 14 and extend in the column direction. Figure 15 This is a cross-sectional view perpendicular to the stacking direction of the plurality of fins 11 of the condenser 3. The fins 13 extend in the same direction relative to the heat transfer tubes 14 extending in the layer direction and are integral. Furthermore, the fins 13 also extend in the column direction. The fins 13 can also be integral fins. The shape of the fins 13 of the evaporator 5 is selected according to the performance of the evaporator 5.

[0077] Next, refer to Figure 1 and Figure 2 The operation of the dehumidification device 1 in Embodiment 1 during dehumidification operation will be explained.

[0078] The superheated refrigerant discharged from the compressor 2 flows into the condenser 3, which is arranged in the air passage 23. The superheated refrigerant flowing into the condenser 3 exchanges heat with the air that has flowed from the external space into the air passage 23 through the suction port 21 and passed through the evaporator 5 arranged in the air passage 23, thereby being cooled and becoming a gas-liquid two-phase refrigerant, which is further cooled to become a subcooled liquid refrigerant.

[0079] On the other hand, the air passing through the condenser 3 arranged in the air passage 23 is heated by exchanging heat with the refrigerant in a superheated gaseous state or a refrigerant in a gas-liquid two-phase state in the condenser 3 after passing through the evaporator 5 also arranged in the air passage 23.

[0080] The subcooled liquid refrigerant flowing from the condenser 3 is depressurized in the pressure reducing device 4 and becomes a gas-liquid two-phase refrigerant before flowing into the evaporator 5 located in the air passage 23. The gas-liquid two-phase refrigerant flowing into the evaporator 5 exchanges heat with the air drawn into the air passage 23 from the suction port 21 and is heated, becoming a superheated gaseous refrigerant. This superheated gaseous refrigerant is then drawn into the compressor 2, compressed by the compressor 2, and discharged again.

[0081] On the other hand, the air passing through the evaporator 5 arranged in the air passage 23, after being drawn into the air passage 23 from the suction port 21, exchanges heat with the refrigerant in the gas-liquid two-phase state in the evaporator 5 and is cooled to a temperature below the dew point of the air and thus dehumidified.

[0082] Next, the effect of the dehumidification device 1 of Embodiment 1 will be explained by comparing it with the comparative example.

[0083] Figure 17 This is a cross-sectional view of the evaporator 5 and condenser 3 in the comparative example dehumidification device 1 along the layer direction. To improve the performance of the evaporator 5, the heat transfer tube 14 of the evaporator 5 is designed as a flat tube with superior heat transfer performance compared to a round tube. However, generally speaking, in a flat tube where the heat transfer tube 14 of the evaporator 5 is flat, dehumidified water tends to accumulate on the surface of the flat tube, hindering heat exchange between the refrigerant and the air within the flat tube. Consequently, the dehumidification capacity of the dehumidification device 1 is reduced. Therefore, in the comparative example dehumidification device 1, it is impossible to improve the performance of the evaporator 5 and increase the dehumidification capacity.

[0084] According to the dehumidification device 1 of this embodiment, the heat transfer tube 14 of the evaporator 5 is a flat tube. Therefore, the performance of the evaporator can be improved. The heat transfer tube 14 of the evaporator 5 extends in the vertical direction. Therefore, it is possible to prevent dehumidifying water from accumulating on the surface of the heat transfer tube 14. As a result, the drainage performance of the evaporator 5 can be improved. Therefore, it is possible to prevent dehumidifying water accumulating on the heat transfer tube 14 of the evaporator 5 from hindering the heat exchange between the refrigerant flowing inside the heat transfer tube 14 and the air. Therefore, the heat transfer performance of the evaporator 5 can be improved. Therefore, the dehumidification capacity of the dehumidification device 1 can be increased.

[0085] Furthermore, by preventing dehumidified water from accumulating on the surface of the heat transfer tubes 14 of the evaporator 5, it is possible to prevent the increase in ventilation resistance caused by the narrowing of the gaps between the heat transfer tubes 14 or between the fins 13 due to the accumulating dehumidified water. As a result, the input of the blower 6 can be reduced, and therefore the input of the dehumidification device 1 can be reduced.

[0086] Furthermore, the heat transfer tube 12 of the condenser 3 extends horizontally, while the heat transfer tube 14 of the evaporator 5 extends vertically. Therefore, the heat transfer tube 12 of the condenser 3 intersects with the heat transfer tube 14 of the evaporator 5. This allows air passing through the heat transfer tube 14 of the evaporator 5 to reliably flow to the heat transfer tube 12 of the condenser 3. Consequently, the heat exchange efficiency between the air and the refrigerant in the condenser 3 can be improved.

[0087] Furthermore, by improving drainage, the dehumidified water condensed on the evaporator 5 is quickly drained into the drain pan 7, thereby reducing the amount of dehumidified water that scatters and remains from the evaporator 5 to the condenser 3. Therefore, it is possible to prevent the dehumidified water remaining in the condenser 3 from being heated and evaporated by the refrigerant flowing in the condenser 3, thus preventing it from rehumidifying the air. Therefore, the dehumidification capacity of the dehumidification device 1 can be further improved.

[0088] Furthermore, according to the dehumidification device 1 of this embodiment, in the condenser 3, the number of refrigerant paths (first refrigerant paths) gradually decreases from upstream to downstream of the refrigerant flow. That is, in the condenser 3, the number of refrigerant paths in the straight section reciprocating between the first head 31 and the second head 32 gradually decreases from the upstream side to the downstream side. Since the pressure loss of the gaseous refrigerant on the upstream side is greater than that of the gas-liquid two-phase refrigerant, the flow velocity can be reduced by increasing the number of refrigerant paths for the gaseous refrigerant on the upstream side, thereby reducing the pressure loss. Furthermore, since the pressure loss of the gas-liquid two-phase refrigerant on the downstream side is smaller than that of the gaseous refrigerant, the flow velocity can be increased by reducing the number of refrigerant paths for the gas-liquid two-phase refrigerant on the downstream side, thereby improving the heat transfer rate.

[0089] Furthermore, according to the dehumidification device 1 of this embodiment, in the evaporator 5, the number of refrigerant paths (the second refrigerant path) gradually increases from upstream to downstream of the refrigerant flow. That is, in the evaporator 5, the number of refrigerant paths in the straight section reciprocating between the first head 34 and the second head 35 gradually increases from the upstream side to the downstream side. Since the pressure loss of the refrigerant in the gas-liquid two-phase state on the upstream side is smaller than that of the refrigerant in the gaseous state, the flow rate can be increased by reducing the number of refrigerant paths for the refrigerant in the gas-liquid two-phase state on the upstream side, thereby improving the heat transfer rate. Furthermore, since the pressure loss of the refrigerant in the gaseous state on the downstream side is larger than that of the refrigerant in the gas-liquid two-phase state, the flow rate can be reduced by increasing the number of refrigerant paths for the refrigerant in the gaseous state on the downstream side, thereby reducing the pressure loss.

[0090] Implementation method 2.

[0091] Reference Figures 18-20 The dehumidification device 1 of Embodiment 2 will be described. The dehumidification device 1 of this embodiment differs from the dehumidification device 1 of Embodiment 1 in that it includes a first condenser 3a, a second condenser 3b, a first intake 21a, a second intake 21b, a partition 8, a first air passage 23a, and a second air passage 23b.

[0092] like Figure 18 and Figure 19 As shown, in the dehumidification device 1 of this embodiment, the housing 20 has a first intake port 21a, a second intake port 21b, a first air passage 23a, and a second air passage 23b. The first intake port 21a is used to draw in air. The first air passage 23a is configured to communicate with the first intake port 21a. The second intake port 21b is used to draw in air. The second air passage 23b is communicated with the second intake port 21b. The second air passage 23b is separated from the first air passage 23a.

[0093] like Figure 19 and Figure 20 As shown, in the dehumidification device 1 of this embodiment, the condenser 3 includes a first condensing section 3a and a second condensing section 3b. The condenser 3 is configured to allow refrigerant to flow in the order of the second condensing section 3b and the first condensing section 3a. The first condensing section 3a and the second condensing section 3b are connected. The refrigerant circuit 101 is configured to circulate refrigerant in the order of compressor 2, second condensing section 3b, first condensing section 3a, pressure reducing device 4, and evaporator 5. The heat transfer tubes 12 of the condenser 3 include heat transfer tubes 12a of the first condensing section 3a and heat transfer tubes 12b of the second condensing section 3b.

[0094] The second condenser section 3b is configured to condense and cool the refrigerant after it has been pressurized by the compressor 2. The second condenser section 3b is a heat exchanger that facilitates heat exchange between the refrigerant and air. The second condenser section 3b has multiple fins 11b and heat transfer tubes 12b. The second condenser section 3b has a refrigerant inlet and an air inlet and an air outlet. In this embodiment, the refrigerant inlet and outlet of the second condenser section 3b are respectively connected to the discharge port of the compressor 2 and the refrigerant inlet of the first condenser section 3a via piping. The heat transfer tubes 12b of the second condenser section 3b are flat tubes.

[0095] The first condenser section 3a is configured to further condense and cool the refrigerant after it has been cooled by the second condenser section 3b. The first condenser section 3a is a heat exchanger that exchanges heat between the refrigerant and air. The first condenser section 3a has multiple fins 11a and heat transfer tubes 12a. The first condenser section 3a has a refrigerant inlet and an outlet, and an air inlet and an outlet. In this embodiment, the refrigerant inlet and outlet of the first condenser section 3a are connected to the outlet of the second condenser section 3b and the inlet of the pressure reducing device 4, respectively, via piping. The heat transfer tubes 12a of the first condenser section 3a are flat tubes.

[0096] In this embodiment, the first condenser section 3a and the second condenser section 3b are flat tube heat exchangers with fins and heat transfer tubes of the same shape. The second condenser section 3b is located above the first condenser section 3a in the layer direction.

[0097] An evaporator 5, a first condenser 3a, and a blower 6 are arranged in the first air passage 23a. The evaporator 5 and the first condenser 3a are arranged in the first air passage 23a such that air drawn in from the first intake port 21a flows in the order of evaporator 5 and first condenser 3a. A second condenser 3b and a blower 6 are arranged in the second air passage 23b. The second condenser 3b is arranged in the second air passage 23b such that air drawn in from the second intake port 21b flows through the second condenser 3b.

[0098] In this 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 upper side in the layer direction compared to the front surface area of ​​the evaporator 5.

[0099] Alternatively, the front surface area of ​​the condenser 3 may be larger than that of the evaporator 5 in the direction of the stacking width of the fins 11 of the condenser 3.

[0100] The first intake port 21a and the second intake port 21b are configured to allow air to enter the interior of the housing 20 from the external space (indoor space). The first air passage 23a is configured to connect the first intake port 21a to the outlet port 22. The second air passage 23b is configured to connect the second intake port 21b to the outlet port 22.

[0101] In this embodiment, the fan 6b rotates around the axis 6a, thereby drawing in air from the external space (indoor space) as shown by arrow A in the figure, which then passes through the evaporator 5 and the first condenser 3a within the first air passage 23a, as shown by arrow B in the figure. Furthermore, the fan 6b rotates around the axis 6a, thereby drawing in air from the external space (indoor space) as shown by arrow A' in the figure, which then passes through the second condenser 3b within the second air passage 23b, as shown by arrow B' in the figure. The air passing through the first air passage 23a and the air passing through the second air passage 23b mix together and are discharged into the external space (indoor space) of the housing 20 through the outlet 22.

[0102] The first air passage 23a and the second air passage 23b can also be separated. The first air passage 23a and the second air passage 23b can be separated, for example, by a partition 8. The first air passage 23a and the second air passage 23b are formed, for example, by the housing 20 and the partition 8. In the airflow direction within the second air passage 23b, the upstream end of the partition 8 is formed at least upstream of the air outlet of the evaporator 5. In the same airflow direction, the downstream end of the partition 8 is formed at least downstream of the air inlet of the evaporator 5. The partition 8 is, for example, formed as a flat plate. The partition 8 is fixed inside the housing 20.

[0103] According to the dehumidification device 1 of this embodiment, the evaporator 5 and the first condenser 3a are arranged in the first air passage 23a, such that air drawn in from the first suction port 21a flows in the order of evaporator 5 and first condenser 3a. The second condenser 3b is arranged in the second air passage 23b, such that air drawn in from the second suction port 21b flows through the second condenser 3b. Therefore, the airflow through the condenser 3 as a whole can be greater than the airflow through the evaporator 5. By increasing the airflow through the condenser 3 as a whole, the heat transfer performance on the condenser 3 side can be improved, and thus the condensation temperature of the refrigerant can be reduced. Furthermore, by reducing the condensation temperature, the difference between the condensation pressure and the evaporation pressure in the refrigerant circuit can be reduced, and thus the input of the compressor 2 can be reduced. As a result, the Energy Factor (EF) value (L / kWh), which is an indicator of the dehumidification performance of the dehumidification device 1 and represents the dehumidification capacity L per kWh, can be improved.

[0104] Furthermore, the material constituting the partition 8 can be made of a material with a lower thermal conductivity than the material of the heat transfer tubes, fins, and head that constitute the refrigerant flowing in the evaporator 5. This reduces the amount of heat exchange that occurs between the air in the first air passage 23a and the air in the second air passage 23b via the partition 8.

[0105] Implementation method 3.

[0106] Reference Figures 21-23 The dehumidification device 1 of Embodiment 3 will now be described. The dehumidification device 1 of this embodiment differs from the dehumidification device 1 of Embodiment 2 in that it includes a third condensation section 3c.

[0107] like Figure 21 and Figure 22 As shown, in the dehumidification device 1 of this embodiment, the condenser 3 includes a first condensing section 3a, a second condensing section 3b, and a third condensing section 3c. The condenser 3 is configured to allow refrigerant to flow in the order of the second condensing section 3b, the first condensing section 3a, and the third condensing section 3c. The third condensing section 3c is connected to the second condensing section 3b. The refrigerant circuit 101 is configured to circulate refrigerant in the order of the compressor 2, the first condensing section 3a, the second condensing section 3b, the third condensing section 3c, the pressure reducing device 4, and the evaporator 5. The heat transfer tube 12 of the condenser 3 includes the heat transfer tube 12c of the third condensing section 3c.

[0108] The first condenser 3a is positioned downstream of the third condenser 3c in the airflow generated by the blower 6. That is, the first condenser 3a is positioned on the downwind side compared to the third condenser 3c.

[0109] like Figure 22 and Figure 23 As shown, the third condenser 3c is configured to further condense and cool the refrigerant cooled by the second condenser 3b. The third condenser 3c is a heat exchanger that exchanges heat between the refrigerant and air. The third condenser 3c has multiple fins 11c and heat transfer tubes 12c. The third condenser 3c has a refrigerant inlet and an outlet, and an air inlet and an outlet. In this embodiment, the refrigerant inlet and outlet of the third condenser 3c are connected to the outlet of the second condenser 3b and the inlet of the pressure reducing device 4, respectively, via piping. The third condenser 3c is positioned upstream of the first condenser 3a in the airflow generated by the blower 6. That is, the third condenser 3c is positioned on the upwind side of the first condenser 3a. Furthermore, the third condenser 3c is positioned downstream of the evaporator 5 in the airflow generated by the blower 6. That is, the third condenser 3c is positioned on the downwind side of the evaporator 5. The heat transfer tube 12c of the third condenser section 3c is a flat tube.

[0110] In this embodiment, the first condenser section 3a, the second condenser section 3b, and the third condenser section 3c are flat-tube heat exchangers with fins and heat transfer tubes of the same shape. The front surface area of ​​the first condenser section 3a and the second condenser section 3b is larger in the upper part of the layer direction than the front surface area of ​​the third condenser section 3c. The front surface area of ​​the third condenser section 3c may also be equivalent to that of the evaporator 5.

[0111] An evaporator 5, a first condenser 3a, a third condenser 3c, and a blower 6 are arranged in the first air passage 23a. The evaporator 5, the first condenser 3a, and the third condenser 3c are arranged within the first air passage 23a such that air drawn in from the first intake 21a flows in the order of evaporator 5, third condenser 3c, and first condenser 3a. A second condenser 3b and a blower 6 are arranged in the second air passage 23b. The second condenser 3b is arranged within the second air passage 23b such that air drawn in from the second intake 21b flows through the second condenser 3b.

[0112] In this embodiment, the fan 6b rotates around the axis 6a. As shown by arrow A in the figure, air drawn in from the external space (indoor space) passes through the evaporator 5, the third condenser 3c, and the first condenser 3a within the first air passage 23a, as shown by arrow B in the figure. Furthermore, the fan 6b rotates around the axis 6a. As shown by arrow A' in the figure, air drawn in from the external space (indoor space) passes through the second condenser 3b within the second air passage 23b, as shown by arrow B' in the figure. The air passing through the first air passage 23a and the air passing through the second air passage 23b mix together and are discharged into the external space (indoor space) of the housing 20 through the outlet 22.

[0113] In the airflow direction within the second air passage 23b, the upstream end of the partition 8 is formed at least upstream of the air outlet of the evaporator 5. In the same airflow direction, the downstream end of the partition 8 is formed at least downstream of the air inlet of the third condenser 3c.

[0114] According to the dehumidification device 1 of this embodiment, the evaporator 5, the first condenser section 3a, and the third condenser section 3c are arranged in the first air passage 23a, such that air drawn in from the first suction port 21a flows in the order of evaporator 5, third condenser section 3c, and first condenser section 3a. The second condenser section 3b is arranged in the second air passage 23b, such that air drawn in from the second suction port 21b flows through the second condenser section 3b. Therefore, by combining the first condenser section 3a, the second condenser section 3b, and the third condenser section 3c, the overall heat transfer area of ​​the condenser 3 can be increased. Therefore, by increasing the overall heat transfer area of ​​the condenser 3, the heat transfer performance on the condenser 3 side can be further improved, thereby reducing the condensation temperature of the refrigerant. Furthermore, by reducing the condensation temperature, the difference between the condensation pressure and the evaporation pressure in the refrigerant circuit can be reduced, thereby reducing the input of the compressor 2. Therefore, it is possible to improve the Energy Factor (L / kWh) value, which represents the dehumidification capacity L per kWh, and is used as an indicator of the dehumidification performance of the dehumidification device 1.

[0115] Furthermore, the material constituting the partition section 8 can be made of a material with a lower thermal conductivity than the materials of the heat transfer tubes, fins, and heads through which the refrigerant flows in the evaporator 5 and the third condenser section 3c. This reduces the amount of heat exchange that occurs between the air in the first air passage 23a and the air in the second air passage 23b via the partition section 8.

[0116] The above-described implementation methods can be appropriately combined.

[0117] The embodiments disclosed herein are illustrative in all respects and should not be considered limiting. The scope of this disclosure is set forth in the claims rather than in the foregoing description, and is intended to include all modifications within the meaning and scope equivalent to the claims.

[0118] Explanation of reference numerals in the attached figures

[0119] 1 Dehumidifier, 2 Compressor, 3 Condenser, 3a First condenser section, 3b Second condenser section, 3c Third condenser section, 4 Pressure reducing device, 5 Evaporator, 6 Blower, 7 Drain pan, 8 Separator, 11, 11a, 11b, 13 Fins, 12, 12a, 12b, 14 Heat transfer tubes, 20 Shell, 21 Suction inlet, 21a First suction inlet, 21b Second suction inlet, 22 Outlet, 23 Air duct, 23a First air duct, 23b Second air duct, 31, 34 First head, 32, 35 Second head, 33, 36 Separator, 101 Refrigerant circuit.

Claims

1. A dehumidification device, wherein, The dehumidification device includes: Casing; and The blower and refrigerant circuit are housed within the casing. The air supply mechanism is used to supply 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 has a first heat transfer tube for the refrigerant to flow through. The evaporator has a second heat transfer tube for the flow of the refrigerant. The condenser is positioned downwind of the evaporator. The first heat transfer tube of the condenser is a flat tube that extends in a horizontal direction. Viewed along this horizontal direction, the first heat transfer tube has a flat cross-sectional shape extending in the direction in which the condenser and the evaporator are arranged. The second heat transfer tube of the evaporator is a flat tube that extends in the vertical direction. When viewed in the vertical direction, the second heat transfer tube has a flat cross-sectional shape that extends in the direction in which the condenser and the evaporator are arranged.

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

3. The dehumidification device according to claim 1 or 2, wherein, The housing has a first intake port for drawing in air, a first air passage communicating with the first intake port, a second intake port for drawing in air, and a second air passage communicating with the second intake port and spaced apart from the first air passage. The condenser has a first condensing section and a second condensing section, and is configured to allow the refrigerant to flow in the order of the second condensing section and the first condensing section. The evaporator and the first condenser are arranged within the first air duct, such that the air drawn in from the first intake port flows in the order of the evaporator and the first condenser. The second condenser is disposed within the second air duct, such that the air drawn in from the second intake port flows through the second condenser.

4. The dehumidification device according to claim 3, wherein, The condenser has a third condensation section and is configured to allow the refrigerant to flow in the order of the second condensation section, the first condensation section, and the third condensation section. The evaporator, the first condenser, and the third condenser are arranged within the first air duct, such that the air drawn in from the first intake port flows in the order of the evaporator, the first condenser, and the third condenser. The second condenser is disposed within the second air duct, such that the air drawn in from the second intake port flows through the second condenser.

Images