CN110139700B - Dehumidifying device - Google Patents
Dehumidifying device Download PDFInfo
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- CN110139700B CN110139700B CN201780072394.3A CN201780072394A CN110139700B CN 110139700 B CN110139700 B CN 110139700B CN 201780072394 A CN201780072394 A CN 201780072394A CN 110139700 B CN110139700 B CN 110139700B
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- 239000003507 refrigerant Substances 0.000 claims abstract description 193
- 238000005192 partition Methods 0.000 claims abstract description 55
- 238000007791 dehumidification Methods 0.000 claims abstract description 44
- 239000007788 liquid Substances 0.000 claims abstract description 24
- 239000013526 supercooled liquid Substances 0.000 claims abstract description 18
- 238000009826 distribution Methods 0.000 claims description 5
- 238000009833 condensation Methods 0.000 abstract description 85
- 230000005494 condensation Effects 0.000 abstract description 85
- 238000010586 diagram Methods 0.000 description 21
- 230000000052 comparative effect Effects 0.000 description 15
- 238000012986 modification Methods 0.000 description 14
- 230000004048 modification Effects 0.000 description 14
- 238000011144 upstream manufacturing Methods 0.000 description 11
- 238000009423 ventilation Methods 0.000 description 5
- 230000007423 decrease Effects 0.000 description 4
- 238000001704 evaporation Methods 0.000 description 4
- 238000004781 supercooling Methods 0.000 description 4
- 230000008020 evaporation Effects 0.000 description 3
- 239000003638 chemical reducing agent Substances 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000007664 blowing Methods 0.000 description 1
- 230000006837 decompression Effects 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
- B01D—SEPARATION
- B01D53/00—Separation of gases or vapours; Recovering vapours of volatile solvents from gases; Chemical or biological purification of waste gases, e.g. engine exhaust gases, smoke, fumes, flue gases, aerosols
- B01D53/26—Drying gases or vapours
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- Analytical Chemistry (AREA)
- General Chemical & Material Sciences (AREA)
- Oil, Petroleum & Natural Gas (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Drying Of Gases (AREA)
Abstract
The dehumidification device (1) is provided with a frame (20), a refrigerant circuit (10), and a blower (6). The condenser (3) includes a 1 st condensation section (3a) through which a refrigerant in a supercooled liquid state flows, a 2 nd condensation section (3b) through which a refrigerant in a gas-liquid two-phase state flows, and a 3 rd condensation section (3c) through which a refrigerant in a superheated gas state flows. The 1 st partition (12) partitions the 1 st air duct (11a) and the 2 nd air duct (11 b). The 2 nd partition (13) has an opening (13a) connecting the 1 st region (22) and the 2 nd region (23). When the opening (13a) of the 2 nd partition (13) is viewed from the 1 st region (22) along the direction in which the shaft (6a) extends, the fan (6b) is disposed within the opening (13 a).
Description
Technical Field
The present invention relates to a dehumidifier, and more particularly, to a dehumidifier including a refrigerant circuit.
Background
In a conventional dehumidification apparatus including a refrigerant circuit, an evaporator and a condenser are arranged in parallel. The evaporator is located upstream of the condenser in the flow of air generated by the blower. In a conventional dehumidifier, air introduced into the dehumidifier is cooled and dehumidified by an evaporator, and the air cooled and dehumidified by the evaporator is heated by a condenser.
As an index indicating the dehumidification performance of the dehumidification device, an EF (Energy Factor) value (L/kWh) indicating the dehumidification amount L per 1kWh is known. The higher the EF value of the dehumidifier, the lower the power consumption. As a method for increasing the EF value of the dehumidification device, it is conceivable to reduce the load on the compressor by lowering the condensation temperature of the refrigerant to reduce the difference between the condensation pressure and the evaporation pressure.
Further, japanese patent laying-open No. 5-87417 (patent document 1) discloses a dehumidifier in which a part of a condenser is disposed in an air passage of air that has undergone heat exchange in an evaporator, and the remaining part of the condenser is disposed in an air passage of air that has not undergone heat exchange in the evaporator.
Documents of the prior art
Patent document
Patent document 1: japanese laid-open patent publication No. 5-87417
Disclosure of Invention
Problems to be solved by the invention
In the conventional dehumidification device, the refrigerant in a superheated gas state, the refrigerant in a gas-liquid two-phase state, and the refrigerant in a supercooled liquid state exchange heat with the air having exchanged heat in the evaporator in the condenser. When the condensation temperature is lowered, the temperature of the air passing through the condenser is also lowered, and therefore, the difference between the temperature of the air passing through the condenser and the condensation temperature is reduced. Therefore, the condensation temperature cannot be sufficiently lowered. Therefore, it is difficult to sufficiently increase the EF value.
In the dehumidification device described in the above-mentioned publication, since the outlet of the refrigerant in the condenser is disposed in the air passage of the air that has not been heat-exchanged in the evaporator, a sufficient degree of supercooling cannot be obtained in the condenser. As a result, in the dehumidification apparatus described in the above-mentioned publication, it is difficult to obtain a large dehumidification amount, and therefore it is difficult to sufficiently increase the EF value.
Further, if the ventilation resistance of the air flowing through the dehumidifier becomes large, the air volume of the blower required to obtain a desired dehumidification amount becomes large, and thus the input (power consumption) of the blower becomes large. Therefore, it is difficult to sufficiently increase the EF value.
The present invention has been made in view of the above problems, and an object thereof is to provide a dehumidifier having a high EF value.
Means for solving the problems
A dehumidifier of the present invention includes a housing, a refrigerant circuit, and a blower. The refrigerant circuit includes a compressor, a condenser, a pressure reducing device, and an evaporator housed inside the casing. The blower has a fan that rotates about a shaft, and is housed inside the housing. In the refrigerant circuit, a refrigerant flows through a compressor, a condenser, a pressure reducing device, and an evaporator in this order. The condenser includes a 1 st condensing part for flowing a refrigerant in a supercooled liquid state, a 2 nd condensing part for flowing a refrigerant in a gas-liquid two-phase state, and a 3 rd condensing part for flowing a refrigerant in a superheated gas state. The frame body includes a 1 st partition and a 2 nd partition. The 1 st partition portion partitions a 1 st air passage in which air introduced from the outside of the housing into the inside passes through the evaporator, the 1 st condenser, and the 2 nd condenser in order by the rotation of the fan about the shaft, and a 2 nd air passage in which air introduced from the outside of the housing into the inside passes through the 3 rd condenser in order by the rotation of the fan about the shaft. The 2 nd partition has an opening portion that connects the 1 st region where the 1 st air passage and the 2 nd air passage partitioned by the 1 st partition are arranged and the 2 nd region where the blower is arranged, and the 2 nd partition partitions the 1 st region and the 2 nd region. When the opening of the 2 nd partition is viewed from the 1 st region along the direction in which the shaft extends, the fan is disposed in the opening.
Effects of the invention
According to the dehumidifier of the present invention, a dehumidifier having a high EF value can be provided.
Drawings
Fig. 1 is a refrigerant circuit diagram of a dehumidifier according to embodiment 1 of the present invention.
Fig. 2 is a schematic diagram showing the configuration of the dehumidifying apparatus according to embodiments 1, 2 and 5 of the present invention.
Fig. 3 is a diagram showing a positional relationship between the fan and the 2 nd partition in embodiment 1 of the present invention.
Fig. 4 is a diagram showing changes in the temperature of the refrigerant and air in the condenser according to embodiment 1 of the present invention.
Fig. 5 is a refrigerant circuit diagram of a dehumidifying apparatus according to a comparative example of embodiment 1 of the present invention.
Fig. 6 is a diagram showing changes in the temperature of the refrigerant and air in the condenser according to the comparative example of embodiment 1 of the present invention.
Fig. 7 is a refrigerant circuit diagram of a dehumidifying apparatus according to variation 1 of embodiment 1 of the present invention.
Fig. 8 is a schematic diagram showing the configuration of a dehumidifying apparatus according to variation 2 of embodiment 1 of the present invention.
Fig. 9 is a diagram showing a positional relationship among the fan, the 2 nd partition portion, and the condenser in modification 2 of embodiment 1 of the present invention.
Fig. 10 is a diagram showing a positional relationship among the fan, the 2 nd partition portion, and the condenser in modification 3 of embodiment 1 of the present invention.
Fig. 11 is a diagram showing a positional relationship between the condenser and the evaporator in the height direction of the condenser in embodiment 2 of the present invention.
Fig. 12 is a diagram showing a positional relationship between the condenser and the evaporator in the width direction of the condenser in embodiment 2 of the present invention.
Fig. 13 is a schematic diagram showing the configuration of a dehumidifier according to embodiment 3 of the present invention.
Fig. 14 is a schematic diagram showing the configuration of a dehumidifier according to embodiment 4 of the present invention.
Fig. 15 is a schematic perspective view showing the configuration of a dehumidifier according to embodiment 4 of the present invention.
Fig. 16 is a schematic diagram showing the configuration of a dehumidifier according to a modification of embodiment 4 of the present invention.
Fig. 17 is a schematic diagram showing the structure of a condenser in embodiment 6 of the present invention.
Fig. 18 is a schematic diagram showing another configuration of a condenser in embodiment 6 of the present invention.
Fig. 19 is a schematic diagram showing the configuration of a dehumidifying apparatus according to embodiment 7 of the present invention.
Fig. 20 is a refrigerant circuit diagram of a dehumidifying apparatus according to embodiment 8 of the present invention.
Detailed Description
Embodiments of the present invention will be described below with reference to the drawings. In the following drawings, the same or corresponding portions are denoted by the same reference numerals, and description thereof will not be repeated.
Referring to fig. 1 and 2, a dehumidification device 1 according to embodiment 1 includes a refrigerant circuit 10, a blower 6, and a housing 20, the refrigerant circuit 10 including a compressor 2, a condenser 3, a pressure reduction device 4, and an evaporator 5, and the housing 20 accommodating the refrigerant circuit 10 and the blower 6 therein. The condenser 3 and the evaporator 5 are heat exchangers that exchange heat between refrigerant and air. The condenser 3 and the evaporator 5 have an inlet and an outlet for refrigerant and an inlet and an outlet for air, respectively. The housing 20 faces an external space (indoor space) to be dehumidified by the dehumidifier 1.
The refrigerant circuit 10 of the dehumidifier 1 is housed inside the casing 20, and constitutes a refrigeration cycle. 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 by pipes. As indicated by arrows in fig. 2, in the refrigerant circuit 10, the refrigerant flows through the compressor 2, the condenser 3, the pressure reducing device 4, and the evaporator 5 in this order.
The compressor 2 sucks and compresses a low-pressure refrigerant, and discharges the refrigerant as a high-pressure refrigerant. The compressor 2 is, for example, an inverter compressor in which the discharge capacity of the refrigerant is variable. The amount of refrigerant circulating in the dehumidifier 1 is controlled by adjusting the discharge capacity of the compressor 2. The compressor 2 has a discharge port and a suction port.
The condenser 3 condenses and cools the refrigerant pressurized by the compressor 2. The condenser 3 includes a 1 st condensing portion 3a through which the refrigerant in a supercooled liquid state flows, a 2 nd condensing portion 3b through which the refrigerant in a liquid-liquid two-phase state flows, and a 3 rd condensing portion 3c through which the refrigerant in a hot gas state flows. The 1 st condensing unit 3a may have a region where the refrigerant in the supercooled liquid state flows, and may have a region where the refrigerant in the supercooled liquid state and in the gas-liquid two-phase state flows. The 3 rd condensing part 3c may have a region where the refrigerant in the superheated gas state flows, or may have a region where the refrigerant in the superheated gas state and the gas-liquid two-phase state flows. In the condenser 3, the refrigerant flows through the 3 rd condensing part 3c, the 2 nd condensing part 3b, and the 1 st condensing part 3a in this order.
The 1 st, 2 nd, and 3 rd condensing portions 3a, 3b, and 3 rd condensing portions 3c have a refrigerant inlet and a refrigerant outlet, respectively. The refrigerant inlet of the 3 rd condensing part 3c is connected to the discharge port of the compressor 2. The refrigerant inlet of the 2 nd condensing part 3b is connected to the refrigerant outlet of the 3 rd condensing part 3 c. The refrigerant inlet of the 1 st condensing part 3a is connected to the refrigerant outlet of the 2 nd condensing part 3 b.
The 1 st condensing unit 3a, the 2 nd condensing unit 3b, and the 3 rd condensing unit 3c may be formed in a single row or a plurality of rows. In the present embodiment, the 1 st condensing unit 3a, the 2 nd condensing unit 3b, and the 3 rd condensing unit 3c are separated from each other via pipes. The 1 st condenser 3a, the 2 nd condenser 3b, and the 3 rd condenser 3c may be integrally formed.
The decompression device 4 decompresses and expands the refrigerant cooled by the condenser 3. The pressure reducing device 4 is, for example, an expansion valve. The expansion valve may also be an electronic expansion valve. The pressure reducing device 4 is not limited to an expansion valve, and may be a capillary tube, for example. The pressure reducing device 4 has a refrigerant inlet and a refrigerant outlet. The refrigerant inlet of the pressure reducing device 4 is connected to the refrigerant outlet of the 3 rd condensing portion 3 c.
The evaporator 5 absorbs heat from the refrigerant expanded by the pressure reducing device 4 to evaporate the refrigerant. The evaporator 5 has a refrigerant inlet and a refrigerant outlet. A refrigerant inlet of the evaporator 5 is connected to a refrigerant outlet of the pressure reducing device 4. The refrigerant outlet of the evaporator 5 is connected to the suction port of the compressor 2. The evaporator 5 is disposed in parallel with the 1 st condensing part 3 a. The evaporator 5 is located upstream of the condenser 3 in the flow of air generated by the blower 6.
The blower 6 is housed inside the housing 20. The blower 6 is configured to introduce air from outside the housing 20 into the inside thereof and to blow the air to the condenser 3 and the evaporator 5. In the present embodiment, the blower 6 includes a fan 6b that rotates about a shaft 6 a. The fan 6B rotates about the shaft 6a, and air introduced from the room as shown by arrows a and C passes through the condenser 3 and the evaporator 5, and is then discharged into the room again as shown by arrow B. In the present embodiment, the blower 6 is disposed downstream of the condenser 3 in the flow of the air generated by the blower 6. In the flow of the air generated by the blower 6, the blower 6 may be disposed between the condenser 3 and the evaporator 5, or may be disposed upstream of the evaporator 5. The number of the air blower 6 may be 1, for example.
The frame 20 includes a 1 st partition 12 that partitions the 1 st air passage 11a and the 2 nd air passage 11 b. The 1 st and 2 nd air passages 11a, 11b are defined by the frame 20 and the 1 st partition 12, respectively. That is, two air passages (air passages) of the 1 st air passage 11a and the 2 nd air passage 11b are provided in the housing 20. The 1 st condenser 3a, the 2 nd condenser 3b, and the evaporator 5 are disposed in the 1 st air passage 11 a. In the 1 st air passage 11a, as shown by an arrow a in the figure, the fan 6b rotates about the shaft 6a, and the air introduced from the outside to the inside of the casing 20 passes through the evaporator 5, the 1 st condenser 3a, and the 2 nd condenser 3b in this order. The 3 rd condenser 3c is disposed in the 2 nd air passage 12. In the 2 nd air passage 11b, as shown by an arrow C in the figure, the fan 6b rotates about the shaft 6a, and the air introduced from the outside to the inside of the casing 20 passes through the 3 rd condenser portion 3C. As shown by arrows a and C in the figure, the flow direction of the air in the 1 st duct 11a and the flow direction of the air in the 2 nd duct 11b are parallel.
Further, the space defining the 1 st duct 11a does not need to be completely separated from the space defining the 2 nd duct 11 b. In the present embodiment, the space defining the 1 st duct 11a is connected to the space defining the 2 nd duct 11b at a position downstream of the 2 nd condenser 3b in the flow direction of the air in the 1 st duct 11 a.
One end (upstream end) of the 1 st partition 12 located on the upstream side in the flow direction of air in the 1 st air passage 11a is disposed on the upstream side of the air outlet of the evaporator 5. The other end (downstream end) of the 1 st partition 12 located downstream in the flow direction of the air in the 2 nd air passage 11b is disposed at the same position as the air outlet of the 1 st condenser 3a or downstream of the air outlet. The 1 st partition portion 12 is formed in a flat plate shape, for example. The 1 st partition 12 is fixed inside the frame 20.
The housing 20 is formed with a 1 st air inlet 14a and a 2 nd air inlet 14b (air inlets 14) for sucking air from an external space (indoor space) to be dehumidified into the housing 20, and a 2 nd air inlet 14a and a 2 nd air inlet 14b (air inlets 14) for blowing air from the inside into the external space, and a blow-out port 21. The frame 20 has a back surface 20a and a front surface 20 b. The back surface 20a is provided with a 1 st suction port 14a and a 2 nd suction port 14 b. The 1 st suction port 14a is configured to suck air into the 1 st air passage 11a on the rear surface 20 a. The 2 nd suction port 14b is configured to suck air into the 2 nd air passage 11b on the rear surface 20 a.
The 1 st suction port 14a is disposed upstream of the air inlet of the evaporator 5 in the 1 st air passage 11a air flow direction. The 2 nd suction port 14b is disposed upstream of the air inlet of the 3 rd condenser 3c in the 2 nd air passage 11b in the flow direction of the air in the 2 nd air passage 11 b.
In the dehumidifier 1, in addition to the 2 nd condenser 3b, the 3 rd condenser 3c, and the evaporator 5 disposed in the 2 nd air passage 11b, any member constituting the refrigerant circuit may be disposed in the 1 st air passage 11 a. For example, the pressure reducer 4 may be disposed in the 1 st air passage 11 a.
The frame 20 includes a 2 nd partition 13 that partitions a 1 st region 22 and a 2 nd region 23. The 1 st region 22 and the 2 nd region 23 are defined by the frame body 20 and the 2 nd partition 13, respectively. That is, two regions, i.e., the 1 st region 22 and the 2 nd region 23, are provided inside the housing 20. In the 1 st region 22, a 1 st air passage 11a and a 2 nd air passage 11b partitioned by the 1 st partition 12 are arranged. That is, the 1 st condenser 3a, the 2 nd condenser 3b and the evaporator 5 disposed in the 1 st air passage 11a are disposed in the 1 st region 22. In addition, the 3 rd condenser 3c disposed in the 2 nd flow path 11b is disposed in the 1 st region 22. The blower 6 is disposed in the 2 nd area 23.
Referring to fig. 2 and 3, the 2 nd partition 13 has an opening 13a connecting the 1 st region 22 and the 2 nd region 23. The 2 nd partition portion 13 is formed in a flat plate shape, for example. When the opening 13a of the 2 nd partition 13 is viewed from the 1 st region 22 along the direction in which the shaft 6a of the blower 6 extends, the fan 6b is disposed in the opening 13 a. The outer diameter D1 of the fan 6b is smaller than the inner diameter D2 of the opening 13 a. The 2 nd partition 13 is configured not to block the suction area of the fan 6 b. In addition, the height of the 2 nd partition 13 is adjusted so that the air flowing from the 1 st area 22 to the 2 nd area 23 passes through the upper end of the 3 rd condensing part 3 c. Therefore, since the heat exchange proceeds to the upper end of the 3 rd condensing part 3c, the heat exchange of the 3 rd condensing part 3c is not hindered.
Next, the operation of the dehumidifying apparatus 1 during the dehumidifying operation will be described with reference to fig. 1, 2, and 4. Fig. 4 is a diagram showing temperature changes of the refrigerant and the air in the condenser 3 of the dehumidifying apparatus 1. In fig. 4, the vertical axis represents the temperature of the refrigerant and air, and the horizontal axis represents the position of the flow path of the refrigerant and air. The circles in fig. 4 represent refrigerant and the triangles represent air. The reference numerals c to f, x2, and y2 in fig. 4 correspond to the positions of the same reference numerals in fig. 1. Reference character c denotes an air inlet of the 1 st condensing part 3 a. Reference numeral d denotes an air inlet of the 2 nd condensing part 3b (an air outlet of the 1 st condensing part 3 a). Reference numeral e denotes an air outlet of the 2 nd condensing portion 3 b. Reference numeral f denotes an air inlet of the 3 rd condensing portion 3 c. Reference numeral g denotes an air outlet of the 3 rd condensing portion 3 c. Reference numeral x2 denotes a refrigerant inlet of the condenser 3. Reference numeral y2 denotes a refrigerant outlet of the condenser 3.
The refrigerant in the superheated gas state discharged from the compressor 2 flows into the 3 rd condenser 3c disposed in the 2 nd flow path 11 b. The refrigerant in the superheated gas state having the temperature T1 and flowing into the 3 rd condenser 3c is cooled by heat exchange with the air having the temperature T6 and introduced into the 1 st air passage 11a from the outside space through the 2 nd suction port 14b, and becomes a refrigerant in a gas-liquid two-phase state having a condensation temperature T2 (39 ℃ in fig. 4). The condensation temperature T2 is at least the temperature T6.
On the other hand, the air having the temperature T6 introduced into the 2 nd air passage 11b is heated by heat exchange with the superheated gaseous refrigerant exceeding the temperature T2 and equal to or lower than the temperature T1 in the 3 rd condenser 3 c. Accordingly, the temperature T7 (50 ℃ in fig. 4) of the air passing through the 3 rd condenser 3c of the 2 nd air passage 11b can be equal to or higher than the condensation temperature T2 of the refrigerant.
The refrigerant in the gas-liquid two-phase state having the temperature T2 and flowing out of the 3 rd condenser 3c flows into the 2 nd condenser 3b disposed in the 1 st flow path 11 a. The gas-liquid two-phase refrigerant having the temperature T2 flowing into the 2 nd condensation unit 3b exchanges heat with air having the temperature T8 passing through the 1 st condensation unit 3 a. The refrigerant in the gas-liquid two-phase state flowing out of the 2 nd condenser 3b flows into the 1 st condenser 3a disposed in the 2 nd flow path 11 b. The refrigerant flowing into the 1 st condenser 3a is further cooled by heat exchange with the air having the temperature T4 passing through the evaporator 5 in the 2 nd air passage 11b, and becomes a supercooled liquid refrigerant having a temperature T3. The supercooled liquid refrigerant flowing out of the 1 st condenser 3a is decompressed by the decompressor 4 to become a two-phase gas-liquid refrigerant, and then flows into the evaporator 5 disposed in the 2 nd flow path 11 b. The refrigerant in the gas-liquid two-phase state flowing into the evaporator 5 is heated by heat exchange with the air introduced into the 2 nd air passage 11b from the outside space through the 1 st suction port 14a, and turns into a superheated gas state refrigerant.
On the other hand, the air introduced into the 2 nd air passage 11b is first cooled to a temperature T4 equal to or lower than the dew point of the air in the evaporator 5, and dehumidified. The cooled and dehumidified air is heated to a temperature T8 by heat exchange with the refrigerant in the supercooled liquid state in the 1 st condensing unit 3 a. The air having the temperature T8 after the heat exchange with the refrigerant in the supercooled liquid state in the 1 st condensation portion 3a is heated to the temperature T5 by the heat exchange with the refrigerant in the gas-liquid two-phase state in the 2 nd condensation portion 3 b.
Accordingly, the temperature T5 of the air passing through the 2 nd air passage 11b can exceed the dew point of the air and be equal to or lower than the condensation temperature of the refrigerant. The temperatures T5 and T7 are set so that the temperature of the outside space is not lowered by the air passing through the 1 st duct 11a and the air passing through the 2 nd duct 11 b.
Next, the operation and effect of the dehumidifier 1 according to the present embodiment will be described in comparison with comparative examples.
Referring to fig. 5, the dehumidification device 1 of the comparative example includes a refrigerant circuit 10 and a housing that houses the refrigerant circuit 10 therein, and the refrigerant circuit 10 causes a refrigerant to flow through the compressor 2, the condenser 3, the pressure reduction device 4, and the evaporator 5 in this order. In the dehumidifier 1 of the comparative example, only an air passage is formed in which the air introduced into the interior passes through the evaporator 5 and the condenser 3 in this order. Fig. 6 is a diagram showing changes in the temperature of the refrigerant and the air in the condenser 3 of the dehumidification device 1 of the comparative example. In fig. 6, the vertical axis represents the temperature of the refrigerant and the air, and the horizontal axis represents the position of the flow path of the refrigerant and the air. The circles in fig. 6 represent refrigerant and the triangles represent air. The reference numerals a, b, x1, y1 of fig. 6 correspond to the positions of the same reference numerals of fig. 5. Reference character a denotes an air inlet of the condenser 3. Reference character b denotes an air outlet of the condenser 3. Reference numeral x1 denotes a refrigerant inlet of the condenser 3. Reference numeral y1 denotes a refrigerant outlet of the condenser 3.
Referring to fig. 5 and 6, in the dehumidifier 1 of the comparative example, the superheated gaseous refrigerant discharged from the compressor 2 flows into the condenser 3. The superheated gas refrigerant having the temperature T1 and flowing into the condenser 3 is cooled by heat exchange with air having a temperature T12 that is introduced into the dehumidifying apparatus 1 from the outside space and cooled while passing through the evaporator 5. The refrigerant is in a gas-liquid two-phase state at a condensation temperature T10 (44 ℃ in fig. 6), and is further cooled to be in a supercooled liquid state at a temperature T11. The condensation temperature T10 and the temperature T11 are at least the temperature T12.
On the other hand, the air having the temperature T12 is heated by heat exchange with the refrigerant in the superheated gas state exceeding the temperature T10 and equal to or lower than the temperature T1, the refrigerant in the gas-liquid two-phase state having the temperature T10, or the refrigerant in the supercooled liquid state having the temperature T11 in the condenser 3. Specifically, the air having the temperature T12 is heated to the temperature T20 by heat exchange with the refrigerant in the supercooled liquid state having the temperature T11 or the refrigerant in the gas-liquid two-phase state having the temperature T10 in the condenser 3, and is then heated to the temperature T13 by heat exchange with the refrigerant in the superheated gas state exceeding the temperature T10 and equal to or lower than the temperature T1 in the condenser 3. Accordingly, the temperature T13 of the air passing through the evaporator 5 and the condenser 3 in this order can be equal to or higher than the condensation temperature T10 of the refrigerant. The temperature T13 is set to be approximately the same as the air temperature in the external space of the dehumidifier 1. Therefore, in the dehumidification device 1 of the comparative example, when the condensation temperature T10 of the refrigerant is lowered, the temperature T13 of the air passing through the condenser 3 is also lowered. In the dehumidification device 1 of the comparative example, the difference between the condensation temperature T10 and the maximum value T20 of the temperature of the air that exchanges heat with the refrigerant in the gas-liquid two-phase state at the condensation temperature T10 becomes small. Therefore, in the dehumidifier 1 of the comparative example, the condensation temperature T10 cannot be sufficiently reduced, and it is difficult to increase the EF value.
In contrast, in the dehumidification device 1 of the present embodiment, in the 3 rd condensation unit 3c, heat exchange is performed between the refrigerant in the superheated gas state and the air at the temperature T6, and the air at the temperature T6 is lower in temperature than the air at the temperature T5 passing through the 2 nd condensation unit 3 b. Therefore, even if the condensation temperature T2 of the refrigerant is lowered, the temperature T7 of the air passing through the 3 rd condensation portion 3c can be suppressed from being lowered. Therefore, according to the dehumidifier 1 of the present embodiment, assuming that the set temperature during the dehumidification operation is the same as that of the dehumidifier 1 of the comparative example, the difference between the condensation temperature T2 and the maximum value T20 of the temperature of the air that exchanges heat with the refrigerant in the gas-liquid two-phase state at the condensation temperature T2 can be made larger than the difference between the condensation temperature T10 and the maximum value T20 of the temperature of the air that exchanges heat with the refrigerant in the gas-liquid two-phase state at the condensation temperature T10. Therefore, in the dehumidifier 1 of the present embodiment, even if the condensation temperature T2 is lowered, the difference between the condensation temperature T2 and the temperature T20 can be made equal to or more than that of the dehumidifier 1 of the comparative example, and therefore the condensation temperature T2 can be lowered as compared with the dehumidifier 1 of the comparative example, and the EF value can be increased.
That is, according to the dehumidifying apparatus 1 of the present embodiment, heat is exchanged between the refrigerant in the superheated gaseous state in the 3 rd condenser portion 3c and the air that has not passed through the evaporator 5 in the 1 st air passage 11 a. Therefore, the condensation temperature of the refrigerant can be reduced without reducing the temperature of the air discharged from the dehumidifier 1, as compared with the dehumidifier 1 of the comparative example in which the heat exchange is performed between the refrigerant in the superheated gas state in the condenser 3 and the air passing through the evaporator 5. As a result, the difference between the condensing pressure and the evaporating pressure can be reduced by lowering the condensing temperature as compared with the dehumidifying apparatus 1 of the comparative example. Therefore, the EF value indicating the dehumidification performance can be increased.
In the 2 nd condenser 3b, heat exchange is performed between the refrigerant in a supercooled liquid state and the air having passed through the evaporator 5. Therefore, the degree of supercooling can be sufficiently obtained as compared with the dehumidification apparatus 1 in which heat exchange is performed between the refrigerant in the supercooled liquid state in the condenser 3 and the air that has not passed through the evaporator 5. Therefore, a large dehumidification amount can be obtained. As a result, in the dehumidifying apparatus 1 of the present embodiment, the EF value indicating the dehumidifying performance becomes high.
When the opening 13a of the 2 nd partition 13 is viewed from the 1 st region 22 along the direction in which the shaft 6a of the blower 6 extends, the fan 6b is disposed in the opening 13 a. Therefore, the 2 nd partition 13 is less likely to obstruct the flow of air from the 1 st area 22 to the 2 nd area 23, and hence the ventilation resistance can be reduced. This can reduce the amount of air supplied to the blower required to obtain a desired amount of dehumidification, and thus can reduce the input (power consumption) of the blower. Therefore, the EF value indicating the dehumidification performance can be sufficiently increased.
Next, a modified example of the present embodiment will be described.
Modified example 1 of the present embodiment will be described with reference to fig. 7. In modification 1 of the present embodiment, the 2 nd condensation unit 3b and the 3 rd condensation unit 3c are integrally configured. That is, the 2 nd condensation unit 3b and the 3 rd condensation unit 3c are not separated from each other via a pipe. On the other hand, the 1 st condensation part 3a and the 2 nd condensation part 3b are separated from each other via a pipe.
According to modification 1 of embodiment 1, since the 2 nd condensation unit 3b and the 3 rd condensation unit 3c are integrally configured, the structure of the condenser 3 can be simplified. In addition, since the 2 nd condensation part 3b and the 3 rd condensation part 3c are integrally configured, the manufacture of the condenser 3 becomes easy.
Next, modification 2 of the present embodiment will be described with reference to fig. 8 and 9. In modification 2 of the present embodiment, when the opening 13a of the 2 nd partition 13 is viewed from the 2 nd area 23 along the direction in which the shaft 6a of the blower 6 extends, the upper end and the lower end of the condenser 3 are disposed in the opening 13 a. The height D3 of the condenser 3 in the vertical direction is smaller than the inner diameter D2 of the opening 13 a.
According to modification 2 of the present embodiment, when the opening 13a of the 2 nd partition 13 is viewed from the 2 nd area 23 along the direction in which the shaft 6a of the blower 6 extends, the upper end and the lower end of the condenser 3 are disposed within the opening 13 a. Therefore, the flow of air from the 1 st area 22 to the 2 nd area 23 in the vertical direction of the condenser 3 is less likely to be obstructed by the condenser 3, and thus the ventilation resistance can be reduced.
Further, a modified example 3 of the present embodiment will be described with reference to fig. 10. In modification 3 of the present embodiment, when the opening 13a of the 2 nd partition 13 is viewed from the 2 nd area 23 along the direction in which the shaft 6a of the blower 6 extends, the upper end and the lower end of the condenser 3 are disposed in the opening 13a, and both ends of the condenser 3 in the left-right direction are disposed in the opening 13 a. The height D3 of the condenser 3 in the vertical direction is smaller than the inner diameter D2 of the opening 13 a. Further, the width D4 of the condenser 3 in the left-right direction is smaller than the inner diameter D2 of the opening 13 a.
According to modification 3 of the present embodiment, when the opening 13a of the 2 nd partition 13 is viewed from the 2 nd area 23 along the direction in which the shaft 6a of the blower 6 extends, the upper end and the lower end of the condenser 3 are disposed in the opening 13a, and both ends of the condenser 3 in the left-right direction are disposed in the opening 13 a. Therefore, the flow of air from the 1 st area 22 to the 2 nd area 23 in the vertical direction and the lateral direction of the condenser 3 is less likely to be obstructed by the condenser 3, and thus the ventilation resistance can be further reduced.
The dehumidifying apparatus 1 according to embodiment 2 has the configuration shown in fig. 2. Fig. 11 is a view showing the heights of the condenser 3 and the evaporator 5. Fig. 12 is a view showing widths of the condenser 3 and the evaporator 5.
Referring to fig. 11 and 12, in dehumidification device 1 according to embodiment 2, condenser 3 is disposed between evaporator 5 and blower 6 and protrudes outward from evaporator 5 when overlapping evaporator 5 in a direction from evaporator 5 toward blower 6.
Specifically, the 2 nd condensation unit 3b and the 3 rd condensation unit 3c are disposed most downstream in the air flow direction. The evaporator 5 is disposed most upstream in the air flow direction. The 1 st condensing unit 3a is disposed between the 2 nd and 3 rd condensing units 3b and 3c and the evaporator 5 in the flow direction of the air. That is, the evaporator 5 is disposed upstream of the 1 st, 2 nd, and 3 rd condensing units 3a, 3b, and 3 rd condensing units 3 c.
The sum of the height h2 of the 2 nd condenser 3b and the height h3 of the 3 rd condenser 3c is greater than the height h1 of the evaporator 5. In the present embodiment, the height h1 of the evaporator 5 is equal to the height h2 of the 2 nd condensing unit 3 b. In addition, the height of the 1 st condensing part 3a is equal to the height h1 of the evaporator 5 and the height h2 of the 2 nd condensing part 3 b. The 3 rd condensing portion 3c protrudes upward from the evaporator 5 in the height direction of the condenser 3.
The width w2 of the 2 nd condensing part 3b is greater than the width w1 of the evaporator 5. In the present embodiment, the width w1 of the evaporator 5 is equal to the width of the 1 st condensing part 3 a. In addition, the width of the 3 rd condensing part 3c is equal to the width w2 of the 2 nd condensing part 3 b. The 2 nd and 3 rd condensing parts 3b and 3c protrude to the right and left sides of the evaporator 5 in the width direction of the condenser 3.
According to the dehumidifying apparatus 1 of the present embodiment, the condenser 3 is disposed between the evaporator 5 and the blower 6 and protrudes outward from the evaporator 5 when overlapping the evaporator 5 in the direction from the evaporator 5 toward the blower 6. Therefore, the air can flow toward the condenser 3 without being hindered by the evaporator 5 in the flow direction of the air from the evaporator 5 toward the blower 6. Therefore, the structure of the air passage is facilitated.
When at least one of the upper and lower portions of the condenser 3 protrudes beyond the evaporator 5, the 2 nd suction port 14b of the 2 nd air passage 11b can be disposed on the rear surface 20a of the housing 20, and the 2 nd air passage 11b can introduce the air from the room into at least one of the upper and lower portions of the condenser 3. In addition, when the condenser 3 protrudes beyond the evaporator 5 in the width direction (left-right direction) of the condenser 3, that is, when the width of the condenser 3 is larger than the width of the evaporator 5, the 2 nd suction port 14b of the 2 nd air passage 11b can be disposed on the rear surface 20a of the housing 20, and the 2 nd air passage 11b can introduce the air from the room into at least one of the left side and the right side of the condenser 3. Therefore, the dehumidifying apparatus 1 of the present embodiment can be configured without greatly changing the configuration of the conventional dehumidifying apparatus.
In addition, the 2 nd suction port 14b of the 2 nd flow path 11b is arranged in alignment with the inlet of the refrigerant of the condenser 3, so that the heat exchange efficiency can be improved. That is, when the flow of the refrigerant in the condenser 3 disposed furthest downstream in the 2 nd flow path 11b is in the vertical direction, the inlet for the high-temperature refrigerant is disposed above the condenser 3. Therefore, the 2 nd air passage 11b is arranged in alignment with the upper portion of the condenser 3, thereby improving the heat exchange efficiency. When the refrigerant in the condenser 3 disposed furthest downstream in the 2 nd flow path 11b flows from the right to the left, the inlet for the high-temperature refrigerant is disposed on the right side of the condenser 3. Therefore, the 2 nd air passage 11b is arranged in alignment with the right side of the condenser 3, thereby improving the heat exchange efficiency.
Referring to fig. 13, in the dehumidifying apparatus 1 according to embodiment 3, the 1 st condensing unit 3a is disposed between the evaporator 5 and the 2 nd condensing unit 3 b. An interval t2 between the 1 st condensing part 3a and the 2 nd condensing part 3b is greater than an interval t1 between the 1 st condensing part 3a and the evaporator 5. That is, the interval t2 between the 1 st condensing part 3a and the 2 nd condensing part 3b in the flow direction of the air from the evaporator 5 toward the blower 6 is larger than the interval t1 between the 1 st condensing part 3a and the evaporator 5. In addition, the interval between the 1 st condensing portion 3a and the 3 rd condensing portion 3c in the flow direction of the air from the evaporator 5 toward the blower 6 is equal to the interval t2 between the 1 st condensing portion 3a and the 2 nd condensing portion 3 b.
Between the evaporator 5 and the 1 st condensing unit 3a, air having a temperature (for example, 13 ℃) lower than room temperature (for example, 27 ℃) after heat exchange with the refrigerant in the evaporator 5 flows toward the 1 st condensing unit 3 a. Between the 1 st condensation unit 3a and the 2 nd condensation unit 3b, the air having a temperature (for example, 28 ℃) higher than the room temperature (for example, 27 ℃) after heat exchange with the refrigerant in the 1 st condensation unit 3a flows toward the 2 nd condenser 3 b.
When the air having passed through the evaporator 5 is mixed with the indoor air between the evaporator 5 and the 1 st condensing part 3a, the difference between the condensing temperature and the air temperature is reduced, and therefore the condenser capacity is reduced, so that the interval t1 between the evaporator 5 and the 1 st condensing part 3a can be made small. On the other hand, between the 1 st condensation part 3a and the 2 nd condensation part 3b, a mixing area of the air having passed through the 1 st condensation part 3a and the outdoor air is provided by increasing the interval t2 between the 1 st condensation part 3a and the 2 nd condensation part 3 b. This increases the difference between the condensation temperature of the 2 nd condensation unit 3b and the air temperature, and therefore, the condensation capacity can be improved.
According to the dehumidification device 1 of the present embodiment, the interval t2 between the 1 st condensation unit 3a and the 2 nd condensation unit 3b is larger than the interval t1 between the 1 st condensation unit 3a and the evaporator 5. Therefore, by suppressing the mixing of the air having passed through the evaporator 5 and the indoor air between the 1 st condensing unit 3a and the evaporator 5, the difference between the condensing temperature of the 1 st condensing unit 3a and the air temperature can be suppressed from decreasing. This can suppress a reduction in condensing capacity. Further, by promoting mixing of the air having passed through the 1 st condensing unit 3a and the indoor air between the 1 st condensing unit 3a and the 2 nd condensing unit 3b, the difference between the condensing temperature of the 2 nd condensing unit 3b and the air temperature can be increased. Thereby, the condensing capacity can be improved. Further, since the run-up region (japanese: run-up region) of the air passing through the 1 st condensation part 3a and the 2 nd condensation part 3b can be provided, the wind speed distribution of the air passing through the 2 nd condensation part 3b can be made uniform.
Referring to fig. 14 and 15, in dehumidification device 1 according to embodiment 4, air inlets for air taken into 2 nd condensation unit 3b and 3 rd condensation unit 3c disposed most downstream in the flow of air are provided in back surface 20a and side surface 20 c.
The 3 rd suction port 15 is provided in the side surface 20c of the housing 20. The 3 rd suction port 15 is configured to suck air into the 1 st duct 11a and the 2 nd duct 11b on the side surface 20 c. The 3 rd suction port 15 is configured to suck indoor air between the 1 st condenser 3a and the 2 nd condenser 3b in the 1 st air passage 11 a. The 3 rd suction port 15 is configured to suck indoor air between the 2 nd suction port 14b and the 3 rd condenser 3c in the 2 nd air passage 11 b.
In the dehumidification device 1 of the present embodiment, as in embodiment 3 described above, the interval t2 between the 1 st condensation unit 3a and the 2 nd condensation unit 3b may be larger than the interval t1 between the 1 st condensation unit 3a and the evaporator 5.
According to the dehumidifying apparatus 1 of the present embodiment, since the casing 20 is provided with the 3 rd suction port 15 for sucking air into the 1 st duct 11a and the 2 nd duct 11b in addition to the 1 st suction port 14a and the 2 nd suction port 14b, the air volume passing through the 2 nd condenser 3b and the 3 rd condenser 3c can be increased. Thereby, the condensing capacity can be improved.
Further, the 1 st suction port 14a, the 2 nd suction port 14b, and the 3 rd suction port 15 can be easily formed by providing openings in the frame 20, and therefore, the dehumidifying apparatus 1 of the present embodiment can be produced without significantly changing the structure of the conventional dehumidifying apparatus.
Next, a dehumidification apparatus 1 according to a modification of embodiment 4 will be described.
Referring to fig. 16, the dehumidification device 1 according to the modification of embodiment 4 includes a 3 rd partition 16, and the 3 rd partition 16 separates air passing through the supercooling section of the 1 st condensation section 3a through which the refrigerant in the supercooled liquid state flows. The 3 rd partition 16 is disposed between the 1 st condenser 3a and the 2 nd condenser 3b so as to block a space between the 1 st condenser 3a and the 2 nd condenser 3 b. The 3 rd suction port 15 is provided above the 3 rd partition 16.
According to the dehumidification device 1 of the modification of embodiment 4, the 3 rd partition 16 suppresses the mixing of the air having a temperature lower than the room temperature and having exchanged heat with the refrigerant in the supercooling portion of the 1 st condensation portion 3a and the air in the room, and thus the condensation capacity can be further improved.
The dehumidifying apparatus 1 according to embodiment 5 has the configuration shown in fig. 2. In the dehumidifying apparatus 1 according to embodiment 5, the refrigerant inlet x2 of the condenser 3 is disposed above the condenser 3, and the refrigerant outlet y2 of the condenser 3 is disposed below the condenser 3. The refrigerant inlet x2 of the condenser 3 is disposed most downstream in the flow of air, and the refrigerant outlet y2 of the condenser 3 is disposed most upstream in the flow of air. That is, the refrigerant inlet x2 of the condenser 3 is provided at the 3 rd condensing part 3c, and the refrigerant outlet y2 of the condenser 3 is provided at the 1 st condensing part 3 a. The refrigerant inlet z of the evaporator 5 is disposed below the evaporator 5.
According to the dehumidification device of the present embodiment, the refrigerant flows through the 3 rd condensation unit 3c, the 2 nd condensation unit 3b, and the 1 st condensation unit 3a in this order. Therefore, the refrigerant flowing through the 3 rd condenser 3c flows in opposition to the air flowing through the 2 nd air passage 11 b. The refrigerant flowing through the 2 nd condenser 3b and the 1 st condenser 3a flows in opposition to the air flowing through the 1 st duct 11a and the air flowing through the 2 nd duct 11 b. This enables heat exchange with high temperature efficiency, and therefore, condensation efficiency can be improved.
Further, since the inlet for the refrigerant is provided in the 3 rd condenser 3c disposed in the 2 nd air passage 11b, the refrigerant having the highest temperature in the condenser 3 can exchange heat with the air having the room temperature flowing through the 2 nd air passage 11 b. Thereby, the heat exchange performance is improved.
Further, since the refrigerant outlet y2 of the condenser 3 is disposed below the condenser 3, the refrigerant outlet y2 of the condenser 3 can be easily connected to the refrigerant inlet z disposed below the evaporator 5. Further, since the refrigerant outlet y2 of the condenser 3 is provided in the 1 st condensing part 3a, the piping connecting the 1 st condensing part 3a and the evaporator 5 can be shortened. Further, the refrigerant flowing through the evaporator 5 can be caused to flow toward the air flowing through the 1 st air passage 11 a. This can improve the evaporation capacity. In addition, in general, the refrigerant flowing through the evaporator 5 flows upward from the bottom in view of flow stability. According to the arrangement of the condenser 3 and the evaporator 5 of the present embodiment, the refrigerant can flow upward in the evaporator 5.
Referring to fig. 17, in dehumidification device 1 according to embodiment 6, the number of divisions of each of 2 nd condensation unit 3b and 3 rd condensation unit 3c is larger than the number of divisions of 1 st condensation unit 3 a. That is, the number of heat transfer tubes through which the refrigerant flows in each of the 2 nd and 3 rd condensing units 3b and 3c is larger than the number of heat transfer tubes through which the refrigerant flows in the 1 st condensing unit 3 a.
As shown in fig. 17, the number of distributions may be changed for each of the 1 st, 2 nd, and 3 rd condensers 3a, 3b, and 3 c. Referring to fig. 18, the number of distributions may be reduced in the middle of the 1 st condensing unit 3 a.
According to the dehumidification device 1 of the present embodiment, the number of divisions of the 2 nd condensation unit 3b and the 3 rd condensation unit 3c is larger than that of the 1 st condensation unit 3 a. Therefore, since the flow velocity of the refrigerant is high in the superheated gas state or the gas-liquid two-phase state, the pressure loss can be reduced by reducing the flow velocity of the refrigerant in a region where the pressure loss is large. On the other hand, since the flow velocity of the refrigerant is low in the supercooled liquid state, the flow velocity of the refrigerant is increased in a region where the pressure loss is small, and thus, high-efficiency heat exchange can be performed.
Embodiment 7
Referring to fig. 19, in the dehumidifying apparatus 1 according to embodiment 7, the 3 rd condenser 3c is configured to extend toward the opposite side of the blower 6 with respect to the 2 nd partition 13 in the 2 nd air passage 11 b.
Since the 1 st condenser 3a, the 2 nd condenser 3b, and the evaporator 5 are disposed in the 2 nd flow path 11b, the pressure loss of the air flowing through the 2 nd flow path 11b is smaller than the pressure loss of the air flowing through the 1 st flow path 11 a. Therefore, the volume of the air flowing through the 2 nd port 11b increases, and the volume of the air flowing through the 1 st port 11a decreases. Therefore, the air volume flowing through the evaporator 5 disposed in the 1 st duct 11a decreases, and the dehumidification amount decreases. For example, if the total of the number of rows and the number of fins of the evaporator 5, the 1 st condensing unit 3a, and the 2 nd condensing unit is equal to the number of rows and the number of fins of the 3 rd condensing unit 3c, the ventilation resistance is equal for the same front surface area. Therefore, the air volume of the air flowing through the 1 st duct 11a and the 2 nd duct 11b can be easily adjusted by the ratio of the front surface area of the evaporator 5, the 1 st condenser 3a, and the 2 nd condenser 3b to the front surface area of the 3 rd condenser.
According to the dehumidifier 1 of the present embodiment, the 3 rd condenser 3c is configured to extend on the opposite side of the blower 6 with respect to the 2 nd partition 13 in the 2 nd air passage 11 b. Therefore, the pressure loss in the 2 nd flow path 11b can be increased. Since the 1 st condenser 3a, the 2 nd condenser 3b, and the evaporator 5 are disposed in the 1 st duct 11a, the pressure loss increases, and therefore, the drift of the air to the 2 nd duct 11b can be suppressed by increasing the pressure loss of the 2 nd duct 11 b. This can suppress a decrease in the dehumidification amount of the evaporator 5. Therefore, the high-efficiency dehumidifying apparatus 1 can be obtained.
Embodiment 8
Referring to fig. 20, in the dehumidifying apparatus 1 according to embodiment 8, the refrigerant circuit 10 is configured to circulate the refrigerant flowing out of the evaporator 5 to the compressor 2 via the condenser 3. In the dehumidification device 1 of the present embodiment, the condenser 3 includes the high-low pressure heat exchange unit 17. The high-low pressure heat exchanger 17 includes a 1 st flow path connecting the refrigerant outlet of the 1 st condenser 3a and the refrigerant inlet of the pressure reducer 4, and a 2 nd flow path connecting the refrigerant outlet of the evaporator 5 and the suction port (refrigerant inlet) of the compressor 2.
In the high-low pressure heat exchange portion 17, heat exchange is performed between the refrigerant flowing through the 1 st flow path and the refrigerant flowing through the 2 nd flow path. Thereby, heat exchange is performed between the refrigerant flowing through the refrigerant outlet of the condenser 3 and the refrigerant flowing through the refrigerant outlet of the evaporator 5. Therefore, the evaporation capacity (dehumidification amount) can be increased by enlarging the enthalpy difference of the refrigerant flowing in the evaporator 5.
In order to maintain reliability, the suction port (refrigerant inlet) of the compressor 2 needs to suck the refrigerant vaporized in the evaporator 5. However, in the evaporator 5, the gas portion of the refrigerant becomes locally high in temperature, and the heat exchange performance is degraded.
In the refrigerant circuit 10 of the present embodiment, even when the refrigerant flowing out of the evaporator 5 is in a gas-liquid two-phase state, the vaporized refrigerant can be returned to the refrigerant suction port of the compressor 2. Therefore, the performance of the evaporator 5 is not degraded, and the reliability of the compressor 2 is not impaired. In addition, even if the refrigerant distribution in the evaporator 5 is poor, the refrigerant in the gas-liquid two-phase state can be caused to flow into the evaporator 5, and therefore the performance of the evaporator 5 can be utilized to the maximum extent.
As described above, according to the dehumidifying apparatus 1 of the present embodiment, the refrigerant circuit 10 is configured to circulate the refrigerant flowing out of the evaporator 5 to the compressor 2 via the condenser 3. Therefore, the liquid refrigerant can be supplied to the region where the heat exchange efficiency is lowered by the generation of the superheated gas in the evaporator 5. Thereby, the heat exchange performance of the evaporator 5 can be improved.
The embodiments disclosed herein are to be considered in all respects as illustrative and not restrictive. The scope of the present invention is defined not by the above description but by the claims, and is intended to include meanings equivalent to the claims and all modifications within the scope.
Description of reference numerals
1 dehumidifier, 2 compressor, 3 condenser, 3a 1 st condensation part, 3b 2 nd condensation part, 3c 3 rd condensation part, 4 decompressor, 5 evaporator, 6 blower, 6a shaft, 6b fan, 10 refrigerant circuit, 11a 1 st air path, 11b 2 nd air path, 12 st partition, 13 nd partition, 13a opening, 14a 1 st suction inlet, 14b 2 nd suction inlet, 15 rd suction inlet, 3 rd suction inlet, 16 rd partition, 17 high-low pressure heat exchanger, 20 frame, 20a back, 20b front, 20c side, 21 blow-out outlet, 22 1 st area, 23 nd area.
Claims (8)
1. A dehumidification device, comprising:
a frame body;
a refrigerant circuit including a compressor, a condenser, a pressure reducing device, and an evaporator, which are housed inside the housing; and
a blower having a fan rotating about a shaft and housed in the interior of the housing,
in the refrigerant circuit, a refrigerant flows through the compressor, the condenser, the pressure reducing device, and the evaporator in this order,
the condenser includes a 1 st condensing part through which the refrigerant in a supercooled liquid state flows, a 2 nd condensing part through which the refrigerant in a gas-liquid two-phase state flows, and a 3 rd condensing part through which the refrigerant in a superheated gas state flows,
the frame body includes:
a 1 st partition that partitions a 1 st air passage in which the air introduced from the outside of the housing into the inside passes through the evaporator, the 1 st condenser, and the 2 nd condenser in order from the outside of the housing by the rotation of the fan about the shaft, and a 2 nd air passage in which the air introduced from the outside of the housing into the inside passes through the 3 rd condenser by the rotation of the fan about the shaft; and
a 2 nd partition having an opening portion that connects a 1 st region where the 1 st air passage and the 2 nd air passage partitioned by the 1 st partition are arranged and a 2 nd region where the blower is arranged, and that partitions the 1 st region and the 2 nd region,
the fan is disposed in the opening when the opening of the 2 nd partition is viewed from the 1 st region in a direction in which the shaft extends,
the circulation direction of the air in the 1 st air passage is parallel to the circulation direction of the air in the 2 nd air passage,
the air passing through the 1 st duct and the air passing through the 2 nd duct are blown out in the same direction by the blower,
the air having passed through the 1 st duct and the air having passed through the 2 nd duct are blown out from the outlet of the housing into the indoor space.
2. The dehumidifying device according to claim 1, wherein the condenser protrudes outward than the evaporator when disposed between the evaporator and the blower and overlapping the evaporator in a direction from the evaporator toward the blower.
3. Dehumidification apparatus according to claim 1 or 2, wherein,
the 1 st condensing part is disposed between the evaporator and the 2 nd condensing part,
the interval between the 1 st condensing part and the 2 nd condensing part is larger than the interval between the 1 st condensing part and the evaporator.
4. Dehumidification apparatus according to claim 1 or 2, wherein,
the frame body comprises a back surface provided with a 1 st suction inlet and a 2 nd suction inlet and a side surface provided with a 3 rd suction inlet,
the rear surface of the housing includes a 1 st suction port configured to suck air into the 1 st air passage and a 2 nd suction port configured to suck air into the 2 nd air passage,
the 3 rd suction port is configured to suck air into the 1 st air passage and the 2 nd air passage on the side surface,
the 3 rd suction port is configured to suck air between the 1 st condenser and the 2 nd condenser in the 1 st air passage.
5. Dehumidification apparatus according to claim 1 or 2, wherein,
in the condenser, a refrigerant flows through the 3 rd condensing part, the 2 nd condensing part, and the 1 st condensing part in this order,
the inlet of the refrigerant is arranged on the upper side of the condenser and is arranged on the 3 rd condensing part,
the outlet of the refrigerant is disposed below the condenser and is disposed in the 1 st condensing part.
6. Dehumidification apparatus according to claim 1 or 2, wherein,
the 2 nd condensing part and the 3 rd condensing part have a distribution number greater than that of the 1 st condensing part.
7. Dehumidification apparatus according to claim 1 or 2, wherein,
the 3 rd condenser is configured to extend toward a side opposite to the blower with respect to the 2 nd partition in the 2 nd air path.
8. Dehumidification apparatus according to claim 1 or 2, wherein,
the refrigerant circuit is configured to circulate the refrigerant flowing out of the evaporator to the compressor via the condenser.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/JP2017/000835 WO2018131121A1 (en) | 2017-01-12 | 2017-01-12 | Dehumidifying device |
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| CN110139700A CN110139700A (en) | 2019-08-16 |
| CN110139700B true CN110139700B (en) | 2021-11-26 |
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| CN201780072394.3A Active CN110139700B (en) | 2017-01-12 | 2017-01-12 | Dehumidifying device |
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| JP (1) | JP6644173B2 (en) |
| CN (1) | CN110139700B (en) |
| TW (1) | TWI671494B (en) |
| WO (1) | WO2018131121A1 (en) |
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| CN113840645A (en) * | 2019-05-27 | 2021-12-24 | 三菱电机株式会社 | Dehumidifier |
| WO2021117199A1 (en) * | 2019-12-12 | 2021-06-17 | 三菱電機株式会社 | Dehumidifier |
| CN115867752A (en) * | 2020-06-05 | 2023-03-28 | 三菱电机株式会社 | Dehumidifier |
| WO2022224416A1 (en) * | 2021-04-22 | 2022-10-27 | 三菱電機株式会社 | Dehumidifying device |
| CN117479998A (en) * | 2021-06-17 | 2024-01-30 | 三菱电机株式会社 | Dehumidifying device |
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- 2017-01-12 JP JP2018561159A patent/JP6644173B2/en active Active
- 2017-01-12 CN CN201780072394.3A patent/CN110139700B/en active Active
- 2017-01-12 WO PCT/JP2017/000835 patent/WO2018131121A1/en active Application Filing
- 2017-04-28 TW TW106114252A patent/TWI671494B/en active
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Also Published As
| Publication number | Publication date |
|---|---|
| TW201825838A (en) | 2018-07-16 |
| WO2018131121A1 (en) | 2018-07-19 |
| JP6644173B2 (en) | 2020-02-12 |
| CN110139700A (en) | 2019-08-16 |
| TWI671494B (en) | 2019-09-11 |
| JPWO2018131121A1 (en) | 2019-06-27 |
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