JPWO2017221351A1 - Dehumidifier - Google Patents

Abstract

Provided is a dehumidifier having an EF value higher than that of a conventional dehumidifier. A refrigerant circuit including a compressor (1), a first condenser (2), a second condenser (3), a pressure reducing device (4), and an evaporator (5); Prepare the body (10). In the refrigerant circuit, the refrigerant flows through the compressor (1), the first condenser (2), the second condenser (3), the pressure reducing device (4), and the evaporator (5) in this order. The housing (10) includes a first air passage (11) through which a part of air taken into the interior from the outside of the housing (10) passes through the first condenser (2), and the housing (10) The remaining portion of the air taken into the interior from the outside includes a partition (6) separating the evaporator and the second air passage (12) sequentially passing through the second condenser (3).

Description

  The present invention relates to a dehumidifying device, and more particularly to a dehumidifying device utilizing a refrigeration cycle.

  A conventional dehumidifier using a refrigeration cycle cools and dehumidifies the air taken into the dehumidifier in the evaporator by the evaporator, and heats the air cooled and dehumidified by the evaporator in the condenser.

  An EF value indicating a dehumidifying amount L per 1 kWh is known as an index indicating the dehumidifying performance of the dehumidifier. The dehumidifier can reduce the power consumption as the EF value is higher. As a method of increasing the EF value of the dehumidifier, it is conceivable to reduce the condensation temperature of the refrigerant to reduce the difference between the condensation pressure and the evaporation pressure and to reduce the load on the compressor.

  In the conventional dehumidifier, since the refrigerant in the superheated gas state, the refrigerant in the gas-liquid two-phase state, and the refrigerant in the supercooling liquid state are heat-exchanged with the air heat-exchanged in the evaporator in the condenser, the condensation temperature is It can not be lowered enough.

  Further, in Japanese Patent Application Laid-Open No. 5-87417 (Patent Document 1), a part of the condenser is formed on the air passage of the heat-exchanged air in the evaporator, and the remaining part of the condenser is heated in the evaporator. A dehumidifier is disclosed which is formed on the air flow path of unexchanged air.

Unexamined-Japanese-Patent No. 5-87417

  However, in the dehumidifying device described in Patent Document 1, the refrigerant outlet in the condenser is formed in the air flow path of the air not heat-exchanged in the evaporator, so that the degree of supercooling in the condenser can be sufficiently obtained. I can not As a result, it is difficult for the dehumidifying device described in Patent Document 1 to obtain a large dehumidifying amount, and it is difficult to sufficiently increase the EF value as compared with the conventional dehumidifying device.

  The present invention has been made to solve the problems as described above. The main object of the present invention is to provide a dehumidifier having a higher EF value than the conventional dehumidifier.

  The dehumidifying device according to the present invention includes a refrigerant circuit including a compressor, a first condenser, a second condenser, a pressure reducing device, and an evaporator, and a housing that accommodates the refrigerant circuit. In the refrigerant circuit, the refrigerant flows through the compressor, the first condenser, the second condenser, the pressure reducing device, and the evaporator in this order. In the case, a part of the air taken into the inside from the outside of the case passes through the first condenser, and the remaining part of the air taken into the inside from the outside of the case is the evaporator, 2 includes a partition that separates the second air passage that sequentially passes through the two condensers. In the first condenser, heat exchange is performed between the refrigerant in the superheated gas state and the air in the first air passage, and in the second condenser, the refrigerant in the supercooled liquid state and the evaporator in the second air passage are passed Heat exchange is performed with the air.

  According to the present invention, it is possible to provide a dehumidifier having a higher EF value than the conventional dehumidifier.

FIG. 1 is a view showing a dehumidifying device according to a first embodiment. It is a graph which shows the temperature change of a refrigerant | coolant and air in the 1st condenser of the dehumidifier which concerns on Embodiment 1, and a 2nd condenser. It is a figure which shows the conventional dehumidification apparatus. It is a graph which shows the temperature change of a refrigerant | coolant and air in the condenser of the dehumidifier shown in FIG. FIG. 7 is a view showing a dehumidifier according to a second embodiment. FIG. 7 is a view showing a dehumidifier according to a third embodiment. FIG. 16 is a graph showing the relationship between the ratio of the air volume of the second air passage to the total air volume of the first air passage and the second air passage of the dehumidifying device according to the fourth embodiment and the EF value. It is a graph which shows the relation between the ratio of the heat transfer area of the 2nd condenser to the total heat transfer area of the 1st condenser of the dehumidifier concerning a 5th embodiment, and the 2nd condenser, and EF value. FIG. 18 is a view showing a dehumidifier according to a sixth embodiment. It is a graph which shows the temperature change of a refrigerant | coolant and air in the 1st condenser of the dehumidifier which concerns on Embodiment 6, and a 2nd condenser.

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

Embodiment 1
Referring to FIG. 1, the dehumidifying device 100 according to the first embodiment includes a compressor 1, a first condenser 2, a second condenser 3, an expansion valve 4 as a pressure reducing device, and a refrigerant circuit including an evaporator 5. And a case 10 housing the refrigerant circuit therein. The first condenser 2, the second condenser 3 and the evaporator 5 are heat exchangers that exchange heat between the refrigerant and the air. Each of the first condenser 2, the second condenser 3 and the evaporator 5 has a refrigerant inlet and an outlet, and an air inlet and an outlet. The housing 10 faces an external space (a room interior space) which the dehumidifying device 100 is to be dehumidified.

  First, the refrigerant circuit of the dehumidifying device 100 will be described. The refrigerant circuit of the dehumidifier 100 constitutes a refrigeration cycle in the housing 10. In the refrigerant circuit, the refrigerant flows through the compressor 1, the first condenser 2, the second condenser 3, the expansion valve 4, and the evaporator 5 in this order. Specifically, the compressor 1 has a discharge port and a suction port. Each of the first condenser 2, the second condenser 3, the expansion valve 4, and the evaporator 5 has a refrigerant inlet and a refrigerant outlet. The refrigerant inlet of the first condenser 2 is connected to the discharge port of the compressor 1. The refrigerant inlet of the second condenser 3 is connected to the refrigerant outlet of the first condenser 2. The refrigerant inlet of the expansion valve 4 is connected to the refrigerant outlet of the second condenser 3. The refrigerant inlet of the evaporator 5 is connected to the refrigerant outlet of the expansion valve 4. The suction port of the compressor 1 is connected to the refrigerant outlet of the evaporator 5. The pressure reducing device is not limited to the expansion valve 4 and may be, for example, a capillary tube.

  The heat transfer area of the first condenser 2 (the sum of the surface areas of the heat transfer tubes in contact with the refrigerant in the first condenser 2) is such that the temperature of the air heat-exchanged in the first condenser 2 is higher than the condensation temperature of the refrigerant Is formed. The heat transfer area of the second condenser 3 (the sum of the surface areas of the heat transfer tubes in contact with the refrigerant in the second condenser 3) is equal to the sum of the heat transfer area of the first condenser 2 and the heat transfer area of the second condenser 3. Preferably, it is 25% or more.

  Next, the air flow path (air path) of the dehumidifying device 100 will be described. Inside the housing 10, at least two air passages of a first air passage 11 and a second air passage 12 are formed. At least a first condenser 2 is disposed in the first air passage 11. At least a second condenser 3 and an evaporator 5 are disposed in the second air passage 12. In the first air passage 11, part of the air taken into the inside from the outside of the housing 10 passes through the first condenser 2. In the second air passage 12, the remaining part of the air taken into the inside from the outside of the housing 10 passes the evaporator 5 and the second condenser 3 in order. The circulation direction of the air in the first air passage 11 is, for example, parallel to the circulation direction of the air in the second air passage 12.

  Specifically, the first air passage 11 is formed between at least the air inlet of the first condenser 2 and the air outlet. The second air passage 12 is formed at least between the air inlet of the evaporator 5 and the air outlet of the second condenser 3. The second air passage 12 is separated from the first air passage 11. That is, the first air passage 11 and the second air passage 12 are prevented from the direct inflow and outflow of air between the two. The second air passage 12 is connected to the first air passage 11 via, for example, a space located upstream of the air inlet of the evaporator 5 in the flow direction of air in the second air passage 12. The first air passage 11 is connected to the second air passage 12 via a space located downstream of the air outlet of the second condenser 3 in the flow direction.

  The first air passage 11 and the second air passage 12 may be separated by any method, but are separated by, for example, the partition portion 6. Each of the first air passage 11 and the second air passage 12 is formed of, for example, the housing 10 and the partition 6. In the air flow direction in the second air passage 12, one end (upstream end) located on the upstream side of the partition 6 is formed at least on the upstream side of the air outlet of the evaporator 5, for example, an evaporator It is formed on the upstream side of a refrigerant pipe connecting the refrigerant outlet 5 and the suction port of the compressor 1. The one end of the partition 6 is formed, for example, on the upstream side of the air inlet of the evaporator 5. In the flow direction, the other end (downstream end) located on the downstream side of the partition 6 is formed downstream of at least the air inlet of the first condenser 2 and the air inlet of the second condenser 3 For example, it is formed on the upstream side of a refrigerant pipe connecting the refrigerant outlet of the first condenser 2 and the refrigerant inlet of the second condenser 3. The other end of the partition 6 is formed, for example, on the downstream side of the air outlet of the first condenser 2 and the air outlet of the second condenser 3. Although the partition part 6 should just be equipped with arbitrary structures, it is formed in flat form, for example. The partition portion 6 is fixed to the inside of the housing 10. The partition part 6 should just be comprised with arbitrary materials.

  The housing 10 has a first opening 13 for introducing air into the interior of the housing 10 from an external space (a room interior space) to be dehumidified, and a second opening for discharging air from the inside to the external space. A portion 14 is formed. The first air passage 11 and the second air passage 12 are formed in parallel between the first opening 13 and the second opening 14. The circulation direction of air in the first air passage 11 and the circulation direction of air in the second air passage 12 are directions from the first opening 13 toward the second opening 14. The first opening 13 is an upstream side of the air inlet of the first condenser 2 in the first air passage 11 in the air flow direction of the first air passage 11 and is an evaporator in the second air passage 12. It is formed upstream of the air inlet 5. The second opening 14 is downstream of the air outlet side of the first condenser 2 in the first air passage 11 in the flow direction, and the air of the second condenser 3 in the second air passage 12. It is formed downstream of the outlet side.

  In the dehumidifying device 100, in the first air passage 11, except for the second condenser 3 and the evaporator 5 disposed in the second air passage 12, any members constituting the refrigerant circuit are arranged. It is good. For example, the compressor 1 may be disposed in the first air passage 11. Further, in the second air passage 12, any member constituting the refrigerant circuit may be disposed except for the first condenser 2 disposed in the first air passage. For example, the expansion valve 4 may be disposed in the second air passage 12.

  Next, with reference to FIG. 1 and FIG. 2, the operation of the dehumidifying device 100 during the dehumidifying operation will be described. FIG. 2 is a graph showing temperature changes of the refrigerant and the air in the first condenser 2 and the second condenser 3 of the dehumidifier 100. The vertical axis of FIG. 2 indicates the temperature of the refrigerant and air, the lower portion of the horizontal axis indicates the flow path of the refrigerant, and the horizontal axis indicates the flow path of the air. In FIG. 2, the refrigerant inlet and the refrigerant outlet of the first condenser 2 are shown as In2 and Out2, and the refrigerant inlet and the refrigerant outlet of the second condenser 3 are shown as In3 and Out3. In FIG. 2, the air inlet and air outlet of the first condenser 2 are shown as In 2 ′ and Out 2 ′, and the air inlet and air outlet of the second condenser 3 are shown as In 3 ′ and Out 3 ′.

  The refrigerant in the superheated gas state discharged from the compressor 1 flows into the first condenser 2 disposed in the first air passage 11. The refrigerant in the superheated gas state of temperature T1 flowing into the first condenser 2 is cooled by heat exchange with the air of temperature T6 taken into the first air passage 11 from the external space through the first opening 13 Thus, the refrigerant becomes a gas-liquid two-phase refrigerant having a condensation temperature T2. The condensation temperature T2 is equal to or higher than the temperature T6.

  On the other hand, the air at temperature T6 taken into the first air passage 11 exchanges heat with the refrigerant in the superheated gas state exceeding temperature T2 and temperature T1 or less in the first condenser 2 or refrigerant in gas-liquid two-phase state at temperature T2. It is heated by being done. Thereby, temperature T7 of the air which passed the 1st condenser 2 of the 1st airway 11 may be made more than condensation temperature T2 of the above-mentioned refrigerant.

  The gas-liquid two-phase refrigerant of temperature T 2 flowing out of the first condenser 2 flows into the second condenser 3 disposed in the second air passage 12. The refrigerant in the gas-liquid two-phase state at temperature T2 that has flowed into the second condenser 3 is further cooled by heat exchange with the air at temperature T4 that has passed through the evaporator 5 in the second air passage 12 to obtain a temperature T3. Of the supercooled liquid state of The refrigerant in the supercooled liquid state which has flowed out of the second condenser 3 is decompressed by passing through the expansion valve 4 and becomes an air-liquid two-phase refrigerant, and then evaporated in the second air passage 12 Flow into the vessel 5. The refrigerant in the gas-liquid two-phase state, which has flowed into the evaporator 5, is heated by heat exchange with the air taken into the second air passage 12 from the external space through the first opening 13 and is in the superheated gas state. It becomes.

  On the other hand, the air taken into the second air passage 12 is dehumidified by being cooled to a temperature equal to or lower than the dew point of the air in the evaporator 5 first. The cooled and dehumidified air is heated by heat exchange with the refrigerant in the gas-liquid two-phase state or the refrigerant in the supercooled liquid state in the second condenser 3. As a result, the temperature of the air that has passed through the second air passage 12 may be above the dew point of the air and below the condensation temperature of the refrigerant. The temperature T5 and the temperature T7 are set so that the temperature of the external space does not decrease due to the air that has passed through the first air passage 11 and the air that has passed through the second air passage 12.

  Next, the operation and effect of the dehumidifier 100 will be described. The dehumidifying device 100 includes a refrigerant circuit including a compressor 1, a first condenser 2, a second condenser 3, a pressure reducing device 4, and an evaporator 5, and a housing 10 accommodating the refrigerant circuit therein. . In the refrigerant circuit, the refrigerant flows through the compressor 1, the first condenser 2, the second condenser 3, the pressure reducing device 4, and the evaporator 5 in this order. Inside the casing 10, a first air passage 11 through which a part of air taken into the interior from the outside of the casing 10 passes the evaporator 5 and the second condenser 3 in this order, and a first air passage 11 and A second air passage 12 is formed, which is separated and the remaining part of the air taken into the inside from the outside of the housing 10 passes through the first condenser 2. In the dehumidifying device 100, heat exchange is performed between the refrigerant in the superheated gas state and the air in the second air passage in the first condenser, and in the second condenser, the refrigerant in the supercooled liquid state and the first air flow Heat exchange is performed between the air passing through the evaporator in the passage and the air.

  In this way, the dehumidifier 100 performs heat exchange between the refrigerant in the supercooled liquid state and the air that has passed through the evaporator 5 in the second condenser 3. Therefore, the dehumidifying device 100 has a degree of supercooling compared to the dehumidifying device described in the above-mentioned Patent Document 1 in which heat exchange is performed between the refrigerant in the supercooled liquid state and the air not passing through the evaporator in the condenser. Can be taken sufficiently, and a large amount of dehumidification can be obtained. As a result, the dehumidifying device 100 has a high EF value indicating dehumidifying performance as compared with the dehumidifying device described in Patent Document 1 above.

  In the first air passage 11, the dehumidifier 100 exchanges heat between the refrigerant in the superheated gas state or the gas-liquid two-phase state in the first condenser 2 and the air not passing through the evaporator 5. To be done. Therefore, the dehumidifying device 100 lowers the temperature of the air taken out of the dehumidifying device 100 as compared with the conventional dehumidifying device in which heat exchange is performed between the refrigerant in the superheated gas state and the air passing through the evaporator in the condenser. The condensation temperature of the refrigerant can be reduced without causing the As a result, the dehumidifying device 100 can reduce the condensation temperature and reduce the difference between the condensing pressure and the evaporation pressure, as compared with the conventional dehumidifying device, and can realize the dehumidifying operation with a high EF value.

  Here, with reference to FIGS. 1 to 4, the difference between the dehumidifying device 100 and the conventional dehumidifying device will be described in more detail. FIG. 3 shows the conventional dehumidifier 200 described above. The conventional dehumidifying device 200 includes a refrigerant circuit in which the refrigerant flows through the compressor 201, the condenser 202, the expansion device 204, and the evaporator 205 in this order, and a housing 210 in which the refrigerant circuit is accommodated. In the conventional dehumidifier 200, only the air passage 211 through which the air taken into the interior passes the evaporator 205 and the condenser 202 in this order is formed. FIG. 4 is a graph showing temperature changes of the refrigerant and the air in the condenser 202 of the dehumidifier 200. The vertical axis of FIG. 4 indicates the temperature of the refrigerant and air, the lower portion of the horizontal axis indicates the flow path of the refrigerant, and the horizontal axis indicates the flow path of the air. In FIG. 4, the refrigerant inlet and the refrigerant outlet of the condenser 202 are shown as In and Out, and the air inlet and the air outlet of the condenser 202 are shown as In 'and Out'. Referring to FIGS. 2 and 4, temperature changes of refrigerant and air in the condenser in the dehumidifier 100 shown in FIG. 1 and the conventional dehumidifier 200 shown in FIG. 3 are compared.

  As shown in FIG. 3 and FIG. 4, in the dehumidifying device 200, the refrigerant in the superheated gas state discharged from the compressor 201 flows into the condenser 202. The refrigerant in the superheated gas state of the temperature T1 which has flowed into the condenser 202 is cooled by being heat-exchanged with the air of the temperature T12 which is taken into the dehumidifier 200 from the external space and passes through the evaporator 205. Be done. The refrigerant is in a gas-liquid two-phase state at a condensing temperature T10, and is further cooled to a supercooled liquid state at a temperature T11. The condensation temperature T10 and the temperature T11 are equal to or higher than the temperature T12.

  On the other hand, the air at temperature T12 is heat-exchanged in the condenser 202 with the refrigerant in the superheated gas state exceeding the temperature T10 and the temperature T1 or less, the gas-liquid two-phase refrigerant at the temperature T10, or the refrigerant in the supercooled liquid state at the temperature T11. It is heated by heating. Specifically, the air at temperature T12 is heated to temperature T20 by heat exchange with the refrigerant in the supercooled liquid state at temperature T11 or in the gas-liquid two-phase state at temperature T10 in the condenser 202. The heat is exchanged with the refrigerant in the superheated gas state in the condenser 202 in the superheated gas state of the temperature T10 or more and the temperature T1 or less, so that the temperature is heated to the temperature T13. Thereby, temperature T13 of the air which passed the evaporator 205 and the condenser 202 in order may be made more than condensation temperature T10 of the said refrigerant | coolant. The temperature T13 is set to be approximately the same as the air temperature of the external space of the dehumidifier 200. Therefore, in the dehumidifying device 200, the difference between the condensing temperature T10 and the maximum value T20 of the temperature of the heat-exchanged refrigerant between the refrigerant in the gas-liquid two-phase state at the condensing temperature T10 decreases. As a result, the dehumidifying device 200 can not sufficiently reduce the contraction temperature T10, and it is difficult to increase the EF value.

  On the other hand, in the dehumidifying device 100, the refrigerant in the superheated gas state or the gas-liquid two-phase state in the first condenser 2 and the air at the temperature T6 lower than the air at the temperature T7 which has passed through the second condenser 3. Heat exchange takes place between the Therefore, according to the dehumidifying device 100, if the set temperature during the dehumidifying operation is made equal to that of the dehumidifying device 200, air that is heat-exchanged with the refrigerant in the gas-liquid two-phase state of the condensing temperature T2 and the condensing temperature T2. The difference between the maximum temperature T20 and the maximum temperature T20 is larger than the difference between the maximum temperature T20 of the temperature of the air heat-exchanged with the refrigerant in the gas-liquid two-phase state at the condensation temperature T10 of the dehumidifier 200 and the condensation temperature T10. can do. As a result, even if the dehumidifying device 100 reduces the condensing temperature T2, the difference between the condensing temperature T2 and the temperature T20 can be made equal to or greater than that of the dehumidifying device 200. It can be lowered and the EF value can be raised.

Second Embodiment
Next, the dehumidifying device 101 according to the second embodiment will be described with reference to FIG. The dehumidifying device 101 basically has the same configuration as the dehumidifying device 100 according to the first embodiment, but a blower unit for taking in air outside the housing 10 to the first air passage 11 and the second air passage 12. It differs in the point further equipped with 15.

  The blower unit 15 is formed in the housing 10. The blower unit 15 is provided to be able to blow the air outside the housing 10 to each of the first air passage 11 and the second air passage 12. The blower unit 15 may be configured of, for example, a single blower. Preferably, the blower unit 15 is formed so as to be capable of adjusting the air volume of the first air passage 11 and the second air passage 12. Preferably, the blower unit 15 includes, for example, a blower provided to be able to blow air to the first air passage 11 and a blower provided to be able to blow air to the second air passage 12.

  According to such a dehumidifying device 101, the air volume of the first air passage 11 and the second air passage 12 can be increased by the air blowing unit 15. In particular, the dehumidifying device 101 can increase the air volume of the first air passage 11 as compared with the dehumidifying device 100, and can sufficiently reduce the condensation temperature of the refrigerant. Such a dehumidifying device 101 has an improved EF value compared to the dehumidifying device 100.

Third Embodiment
Next, the dehumidifying device 102 according to the third embodiment will be described with reference to FIG. The dehumidifying device 102 basically has the same configuration as the dehumidifying device 100 according to the first embodiment, but an adjustment unit that adjusts the ratio of the air volume in the first air passage 11 and the air volume in the second air passage 12 It differs in the point provided with 16 further.

  The adjustment unit 16 is formed in the housing 10. The adjustment unit 16 may have any configuration as long as the air volume in the first air passage 11 and the air volume in the second air passage 12 can be adjusted. The adjusting unit 16 is, for example, a damper which is formed in the first air passage 11 and is capable of adjusting the cross-sectional area (opening degree) of the first air passage 11 perpendicular to the flow direction of the air of the first air passage 11. . The adjustment unit 16 is formed, for example, on the upstream side of the first condenser 2 in the first air passage 11.

  The first air passage 11 in which the first condenser 2 is disposed has a structure that is a resistor to air in comparison with the second air passage 12 in which the second condenser 3 and the evaporator 5 are disposed. Few. Therefore, when the air volume adjustment between the first air passage 11 and the second air passage 12 is not performed by, for example, the blower unit 15 shown in FIG. 5, the air volume of the first air passage 11 is the air volume of the second air passage 12 The condensation temperature can not be sufficiently lowered because the temperature is more than that. On the other hand, the dehumidifier 102 can restrict the air volume of the first air passage 11 by adjusting the air volume of the first air passage 11 and the second air passage 12 by the adjusting unit 16. Therefore, the dehumidifying device 102 can sufficiently reduce the condensing temperature as compared with the dehumidifying device not provided with the adjusting unit 16, and the EF value is high.

  The dehumidifier 102 preferably further includes a blower 15 as shown in FIG. In this case, the blower unit 15 may be a single blower, and the blower unit 15 may be configured such that the air volume adjustment between the first air passage 11 and the second air passage 12 can not be performed. In this way, the dehumidifying device 102 can increase the air volume of the first air passage 11 and the second air passage 12 by the air blower 15 and can adjust each air volume by the adjusting device 16, so Compared with the dehumidifier which does not have the part 15 and the adjustment part 16, the condensation temperature can be sufficiently lowered and the EF value is high.

Embodiment 4
Next, the dehumidifying device according to the fourth embodiment will be described. The dehumidifying device according to the fourth embodiment basically has the same configuration as the dehumidifying device 100 according to the first embodiment, but the air volume of the second air passage 12 is the first air passage 11 and the second air passage. It differs in that it is specified that it is 30% or more and 68% or less of the total air volume of 12.

  FIG. 7 is a graph showing the relationship between the ratio of the air volume of the second air passage 12 to the total air volume of the first air passage 11 and the second air passage 12 calculated by simulation and the EF value of the dehumidifying device 100. . The horizontal axis in FIG. 7 indicates the ratio (unit:%) of the air volume of the second air passage 12 to the total air volume of the first air passage 11 and the second air passage 12. The vertical axis of FIG. 7 shows the ratio (unit:%) of the EF value of the dehumidifier 100 to the EF value of the conventional dehumidifier 200 shown in FIG. As shown in FIG. 7, when the ratio of the air volume of the second air passage 12 to the total air volume of the first air passage 11 and the second air passage 12 is 30%, 50%, 68%, the above ratio of the EF value is 110 %, 118%, 116%.

  The dehumidifier in which the ratio of the air volume of the second air passage 12 is 30% or more and 68% or less is the amount of heat exchange with the air passing through the evaporator 5 in the second condenser 3 as compared with the conventional defroster. Since the condensation temperature can be sufficiently reduced, the EF value is improved as compared with the conventional defroster.

Fifth Embodiment
Next, the dehumidifying device according to the fifth embodiment will be described. The dehumidifying device according to the fifth embodiment basically has the same configuration as the dehumidifying device 100 according to the first embodiment, but the material constituting the partition 6 is a transmission through which the refrigerant flows in the first condenser 2 It differs in that it is specified that the material has a lower thermal conductivity than the material that constitutes the heat pipe (not shown).

  The material constituting the partition portion 6 may be any material having a thermal conductivity lower than that of the material constituting a heat transfer pipe (not shown) through which the refrigerant flows in the first condenser 2. For example, resin, ceramics, It is at least one selected from the group consisting of paper, rubber and the like.

  In this way, it is possible to suppress heat exchange between the air in the first air passage 11 and the air in the second air passage 12 through the partition portion 6. Therefore, it is possible to suppress the temperature decrease of the air flowing to the first condenser 2 in the first air passage 11, and to suppress the temperature increase of the air passing through the evaporator 5 in the second air passage 12. Can. As a result, according to the dehumidifying device according to the fifth embodiment, the material forming the partition portion 6 is a material having the same thermal conductivity as the material forming the heat transfer tube through which the refrigerant flows in the first condenser 2 The EF value is higher than in the case.

Sixth Embodiment
Next, the dehumidifying device according to the sixth embodiment will be described. The dehumidifying device according to the sixth embodiment basically has the same configuration as the dehumidifying device 100 according to the first embodiment, but the heat transfer area of the first condenser 2 is the heat transfer area of the second condenser 3 It differs in that it is identified that it is larger than it.

  FIG. 8 shows the ratio of the heat transfer area of the second condenser 3 to the sum of the heat transfer area of the first condenser 2 and the heat transfer area of the second condenser 3 calculated by simulation, and the EF of the dehumidifier 100 It is a graph which shows a relation with a value. The horizontal axis of FIG. 8 indicates the ratio (unit:%) of the heat transfer area of the second condenser 3 to the sum of the heat transfer areas of the first condenser 2 and the second condenser 3. The vertical axis of FIG. 8 shows the ratio (unit:%) of the EF value of the dehumidifier 100 to the EF value of the conventional dehumidifier 200 shown in FIG. As shown in FIG. 8, the dehumidifier has a ratio of the heat transfer area of the second condenser 3 to the sum of the heat transfer area of the first condenser 2 and the heat transfer area of the second condenser 3 of 32% or more. The above-mentioned ratio of the EF value is 105% or more, and the EF value is improved as compared with the conventional dehumidifier. In particular, the dehumidifying apparatus in which the ratio of the heat transfer area of the second condenser 3 to the sum of the heat transfer area of the first condenser 2 and the heat transfer area of the second condenser 3 is 50% or more Is 115% or more, and the EF value is improved as compared with the conventional dehumidifier.

Seventh Embodiment
Next, a dehumidifying device 103 according to a seventh embodiment will be described with reference to FIG. 9 and FIG. The dehumidifying device 103 basically has the same configuration as the dehumidifying device 100 according to the first embodiment, but is connected in series with the second air passage 12 inside the housing 10, The difference is that a third air passage 17 through which the air having passed through the vessel 3 passes through the first condenser 2 is further formed.

  The first condenser 2 is a first heat exchange unit in which the refrigerant in the superheated gas state is heat-exchanged with the air not passing through the evaporator 5, the refrigerant in the gas-liquid two-phase state is the evaporator 5, the second condenser And a second heat exchange unit (a heat exchange unit positioned downstream of the first heat exchange unit in the flow direction of the refrigerant) that exchanges heat with the air that has sequentially passed through 3.

  The second air passage 12 is formed between the air inlet of the evaporator 5 and the air outlet of the second condenser 3. The third air passage 17 is formed between the air outlet of the second condenser 3 and the air outlet of the second heat exchange unit of the first condenser 2. The first air passage 11 is separated by, for example, the second air passage 12 and the third air passage by the divider 6. The downstream end of the partition 6 is connected to the air inlet of the first condenser 2 so as to separate, for example, the first condenser 2 into the first heat exchange section and the second heat exchange section.

  FIG. 10 is a graph showing temperature changes of the refrigerant and air in the first condenser 2 and the second condenser 3 of the dehumidifier 103. The vertical axis in FIG. 10 indicates the temperature of the refrigerant and air, the lower portion of the horizontal axis indicates the flow path of the refrigerant, and the horizontal axis indicates the flow path of the air. In FIG. 10, the refrigerant inlet and the refrigerant outlet of the first condenser 2 are shown as In2 and Out2, and the refrigerant inlet and the refrigerant outlet of the second condenser 3 are shown as In3 and Out3. In FIG. 10, the air inlets and air outlets of the first heat exchange unit of the first condenser 2 are In2′a and Out2′a, and the air inlet and air outlets of the second heat exchange unit of the first condenser 2 are In2 ′. b and Out2'b, the air inlet and air outlet of the second condenser 3 are shown as In3 'and Out3'.

  Even in this case, as shown in FIGS. 9 and 10, heat exchange is performed between the refrigerant in the supercooled liquid air state and the air that has passed through the evaporator 5 in the second heat exchange section of the second condenser 3. As compared with the dehumidifying device described in the above-mentioned Patent Document 1, the dehumidifying device 103 performs heat exchange between the refrigerant in the supercooled liquid state and the air not passing through the evaporator in the condenser. A sufficient degree of subcooling can be obtained, and a large amount of dehumidification can be obtained.

  Moreover, since the amount of the air which passes the 2nd condenser 3 increases compared with the dehumidifier 100, such a dehumidifier 103 is improving the condensing capability. Furthermore, as shown in FIG. 10, in the dehumidifying device 103, the air having a temperature T8 close to the subcooling temperature of the refrigerant that has passed through the second condenser 3 is the refrigerant in the gas-liquid two-phase state in the first condenser 2. Since the heat exchange can be performed, the condensing capacity is enhanced compared to the dehumidifier 100.

  In the dehumidifying device 103, as long as the first air passage 11 and the second air passage 12 are separated, the first air passage 11 and the third air passage 17 may not be separated. As shown in FIG. 10, the temperature T8 of the air that has passed through the second air passage 12 may be, for example, substantially equal to the temperature T6 of the air taken into the first air passage. Therefore, even if the air passing through the second air passage 12 and flowing in the third air passage 17 mixes in the first air passage 11, the same effect as the dehumidifying device 103 can be obtained.

  It should be understood that the embodiment disclosed herein is illustrative and non-restrictive in every respect. The scope of the present invention is shown not by the above description but by the scope of claims, and is intended to include all modifications within the scope and meaning equivalent to the scope of claims.

  DESCRIPTION OF SYMBOLS 1 compressor, 2 1st condenser, 3 2nd condenser, 4 expansion valve (pressure reduction apparatus) 5 evaporator, 6 partitions, 10 housings, 11 1st air path, 12 2nd air path, 13 1st Opening part, 14 2nd opening part, 15 ventilation part, 16 adjustment part, 17 3rd air path, 100, 101, 102, 103 Dehumidifier.

Claims (6)

A refrigerant circuit including a compressor, a first condenser, a second condenser, a pressure reducing device, and an evaporator, and a case containing the refrigerant circuit therein.
In the refrigerant circuit, the refrigerant flows through the compressor, the first condenser, the second condenser, the pressure reducing device, and the evaporator in this order,
The casing includes a first air passage through which a part of air taken into the interior from the outside of the casing passes through the first condenser, and a remaining portion of the air taken into the interior from the outside of the casing. A partition part separating the evaporator and a second air passage sequentially passing through the second condenser;
In the first condenser, heat exchange is performed between the refrigerant in the superheated gas state and the air in the first air path, and in the second condenser, the refrigerant in the supercooled liquid state and the second air path A dehumidifier, wherein heat exchange is performed between the air passing through the evaporator and the inside. A blower which is accommodated inside the casing and takes in air outside the casing into the first air passage and the second air passage;
The dehumidifier according to claim 1, further comprising: an adjusting unit accommodated in the housing and adjusting a ratio of an air volume in the first air passage and an air volume in the second air passage. .   The dehumidifier according to claim 1 or 2, wherein the air volume of the second air passage is 30% or more and 68% or less of the total air volume of the first air passage and the second air passage.   The dehumidifying device according to any one of claims 1 to 3, wherein a material forming the partition portion has a thermal conductivity lower than that of a material forming a heat transfer pipe through which the refrigerant flows in the first condenser. apparatus.   The dehumidifier according to any one of claims 1 to 4, wherein a heat transfer area of the first condenser is larger than a heat transfer area of the second condenser.   A third air passage, which is connected in series with the second air passage and in which the air having passed through the second condenser passes through the first condenser, is further formed inside the housing. The dehumidification apparatus of any one of Claims 1-5.

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