JP6644173B2 - Dehumidifier - Google Patents

Description

  The present invention relates to a dehumidifier, and more particularly to a dehumidifier provided with a refrigerant circuit.

  In a conventional dehumidifier having 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. A conventional dehumidifier cools and dehumidifies air taken into the dehumidifier in an evaporator, and heats air cooled and dehumidified in the evaporator in a condenser.

  As an index indicating the dehumidifying performance of the dehumidifying device, an EF (Energy Factor) value (L / kWh) indicating a dehumidifying amount L per 1 kWh is known. The dehumidifier can reduce the power consumption as the EF value increases. As a method of increasing the EF value of the dehumidifying 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.

  Japanese Patent Application Laid-Open No. 5-87417 (Patent Document 1) discloses that a part of a condenser is disposed in an air passage of air heat exchanged in an evaporator, and the remaining part of the condenser is heated in an evaporator. A dehumidifier is disclosed that is located in the air path of the air that has not been replaced.

JP-A-5-87417

  In a conventional dehumidifier, a refrigerant in a superheated gas state, a refrigerant in a gas-liquid two-phase state, and a refrigerant in a supercooled liquid state are heat-exchanged with air exchanged in an evaporator in a condenser. When the condensing temperature is reduced, the temperature of the air that has passed through the condenser also decreases, so that the difference between the temperature of the air that has passed through the condenser and the condensing temperature decreases. Therefore, the condensation temperature cannot be sufficiently reduced. Therefore, it is difficult to sufficiently increase the EF value.

  Further, in the dehumidifier described in the above publication, the outlet of the refrigerant in the condenser is arranged in the air path of the air that has not been heat-exchanged in the evaporator, so that the supercooling degree cannot be sufficiently obtained in the condenser. . As a result, with the dehumidifier described in the above publication, it is difficult to obtain a large amount of dehumidification, and thus it is difficult to sufficiently increase the EF value.

  Also, when the ventilation resistance of the air flowing in the dehumidifier increases, the air flow of the blower required to obtain a desired amount of dehumidification increases, so that the input (power consumption) of the blower increases. 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 of the present invention is to provide a dehumidifier having a high EF value.

  The dehumidifier of the present invention includes a housing, a refrigerant circuit, and a blower. The refrigerant circuit includes a compressor, a condenser, a decompression device, and an evaporator housed inside the housing. The blower has a fan that rotates about an axis, and is housed inside a housing. In the refrigerant circuit, the refrigerant flows through the compressor, the condenser, the pressure reducing device, and the evaporator in order. The condenser includes a first condenser through which the refrigerant in the supercooled liquid state flows, a second condenser through which the refrigerant in the gas-liquid two-phase state flows, and a third condenser through which the refrigerant in the superheated gas state flows. The housing includes a first partition and a second partition. A first airflow passage through which the air taken in from the outside of the housing by the rotation of the fan around the shaft passes through the evaporator, the first condenser, and the second condenser in order; When the fan rotates around the axis, the air taken in from the outside of the housing to the inside separates the second air passage passing through the third condensing portion. The second partition has an opening that connects the first area where the first air path and the second air path partitioned by the first partition are arranged and the second area where the blower is arranged, and The first area and the second area are partitioned. When the opening of the second partition is viewed from the first region along the direction in which the axis extends, the fan is disposed in the opening.

  According to the dehumidifier of the present invention, a dehumidifier having a high EF value can be provided.

FIG. 2 is a refrigerant circuit diagram of the dehumidifier according to Embodiment 1 of the present invention. It is the schematic which shows the structure of the dehumidifier which concerns on Embodiment 1, 2 and 5 of this invention. FIG. 3 is a diagram illustrating a positional relationship between a fan and a second partition according to the first embodiment of the present invention. 3 is a graph showing temperature changes of refrigerant and air in the condenser according to Embodiment 1 of the present invention. FIG. 3 is a refrigerant circuit diagram of a dehumidifier according to a comparative example of Embodiment 1 of the present invention. 4 is a graph showing temperature changes of refrigerant and air in a condenser according to a comparative example of Embodiment 1 of the present invention. FIG. 3 is a refrigerant circuit diagram of a dehumidifier according to a first modification of the first embodiment of the present invention. It is the schematic which shows the structure of the dehumidifier which concerns on the modification 2 of Embodiment 1 of this invention. FIG. 7 is a diagram showing a positional relationship among a fan, a second partition, and a condenser according to a second modification of the first embodiment of the present invention. FIG. 9 is a diagram showing a positional relationship among a fan, a second partition, and a condenser according to a third modification of the first embodiment of the present invention. It is a figure which shows the positional relationship of the condenser in the height direction of the condenser and the evaporator in Embodiment 2 of this invention. It is a figure which shows the positional relationship of the condenser in the width direction of the condenser and the evaporator in Embodiment 2 of this invention. It is the schematic which shows the structure of the dehumidifier which concerns on Embodiment 3 of this invention. It is the schematic which shows the structure of the dehumidifier which concerns on Embodiment 4 of this invention. It is a schematic perspective view which shows the structure of the dehumidifier which concerns on Embodiment 4 of this invention. It is the schematic which shows the structure of the dehumidifier which concerns on the modification of Embodiment 4 of this invention. FIG. 13 is a schematic diagram illustrating a configuration of a condenser according to Embodiment 6 of the present invention. FIG. 15 is a schematic diagram illustrating another configuration of a condenser according to Embodiment 6 of the present invention. It is the schematic which shows the structure of the dehumidifier which concerns on Embodiment 7 of this invention. It is a refrigerant circuit diagram of the dehumidifier concerning Embodiment 8 of this invention.

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

Embodiment 1 FIG.
1 and 2, a dehumidifier 1 according to Embodiment 1 includes a refrigerant circuit 10 including a compressor 2, a condenser 3, a decompression device 4, and an evaporator 5, a blower 6, and a refrigerant circuit 10. And a housing 20 that houses the blower 6 therein. The condenser 3 and the evaporator 5 are heat exchangers that perform heat exchange between refrigerant and air. Each of the condenser 3 and the evaporator 5 has a refrigerant inlet and an outlet, and an air inlet and an outlet. 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 housing 20 and forms a refrigeration cycle. The refrigerant circuit 10 is configured by connecting the compressor 2, the condenser 3, the decompression device 4, and the evaporator 5 sequentially with piping. As shown 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 order.

  The compressor 2 sucks and compresses the low-pressure refrigerant, and discharges it as a high-pressure refrigerant. The compressor 2 is, for example, an inverter compressor having a variable refrigerant discharge capacity. The refrigerant circulation amount 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 first condenser 3a through which the supercooled liquid refrigerant flows, a second condenser 3b through which the gas-liquid two-phase refrigerant flows, and a third condenser 3c through which the superheated gas refrigerant flows. Contains. The first condensing section 3a only needs to have an area through which the refrigerant in the supercooled liquid state flows, and may have an area through which the refrigerant in the supercooled liquid state and the gas-liquid two-phase state flows. The third condensing section 3c only needs to have a region in which the refrigerant in the superheated gas state flows, and may have a region in which the refrigerant in the superheated gas state and the refrigerant in the gas-liquid two-phase state flow. In the condenser 3, the refrigerant flows through the third condenser 3c, the second condenser 3b, and the first condenser 3a in this order.

  Each of the first condenser 3a, the second condenser 3b, and the third condenser 3c has a refrigerant inlet and a refrigerant outlet. The refrigerant inlet of the third condenser 3c is connected to the outlet of the compressor 2. The refrigerant inlet of the second condenser 3b is connected to the refrigerant outlet of the third condenser 3c. The refrigerant inlet of the first condenser 3a is connected to the refrigerant outlet of the second condenser 3b.

  The first condensing unit 3a, the second condensing unit 3b, and the third condensing unit 3c may be configured in a single row or a double row. In the present embodiment, the first condenser 3a, the second condenser 3b, and the third condenser 3c are separated from each other via a pipe. The first condensing section 3a, the second condensing section 3b, and the third condensing section 3c may be integrally formed.

  The decompression device 4 decompresses and expands the refrigerant cooled in the condenser 3. The pressure reducing device 4 is, for example, an expansion valve. This expansion valve may be an electronic expansion valve. The pressure reducing device 4 is not limited to an expansion valve, and may be, for example, a capillary tube. 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 third condenser 3c.

  The evaporator 5 causes the refrigerant expanded by the pressure reducing device 4 to absorb heat and evaporate the refrigerant. The evaporator 5 has a refrigerant inlet and a refrigerant outlet. The refrigerant inlet of the evaporator 5 is connected to the refrigerant outlet of the decompression device 4. The refrigerant outlet of the evaporator 5 is connected to the suction port of the compressor 2. The evaporator 5 is arrange | positioned along with the 1st condensing part 3a. 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 take in the air outside the housing 20 and blow the air to the condenser 3 and the evaporator 5. In the present embodiment, the blower 6 has a fan 6b that rotates around a shaft 6a. When the fan 6b rotates about the shaft 6a, air taken in from the room passes through the condenser 3 and the evaporator 5 as shown by arrows A and C in the figure, and then as shown by arrow B in the figure. Is exhaled again into the room. In the present embodiment, blower 6 is arranged downstream of condenser 3 in the flow of air generated by blower 6. The blower 6 may be arranged between the condenser 3 and the evaporator 5 or may be arranged upstream of the evaporator 5 in the flow of air generated by the blower 6. The number of the blowers 6 may be one, for example.

  The housing 20 includes a first partition 12 that partitions the first air passage 11a and the second air passage 11b. Each of the first air passage 11 a and the second air passage 11 b is defined by the housing 20 and the first partition 12. That is, two air passages (air passages) of the first air passage 11a and the second air passage 11b are provided inside the housing 20. A first condenser 3a, a second condenser 3b, and an evaporator 5 are arranged in the first air passage 11a. In the first air passage 11a, as shown by an arrow A in the figure, when the fan 6b rotates about the shaft 6a, the air taken in from the outside of the casing 20 into the evaporator 5, the first condenser 3a. And the second condensing part 3b. In the second air passage 12, a third condenser 3c is arranged. In the second air passage 11b, as shown by an arrow C in the figure, the air taken in from the outside of the housing 20 when the fan 6b rotates around the shaft 6a passes through the third condenser 3c. As shown by arrows A and C in the figure, the flow direction of the air in the first air passage 11a is parallel to the flow direction of the air in the second air passage 11b.

  The space defining the first air passage 11a does not need to be completely separated from the space defining the second air passage 11b. In the present embodiment, the space that defines the first air passage 11a is a space that defines the second air passage 11b downstream of the second condensing section 3b in the direction of air flow in the first air passage 11a. It is connected.

  One end (upstream end) located on the upstream side of the first partition 12 in the direction of flow of the air in the first air passage 11 a is arranged on the upstream side of the air outlet of the evaporator 5. In the flow direction of the air in the second air passage 11b, the other end (downstream end) located downstream of the first partition 12 is located at the same position as the air outlet of the first condenser 3a or downstream from the air outlet. Located on the side. The first partition 12 is formed, for example, in a flat plate shape. The first partition 12 is fixed inside the housing 20.

  The housing 20 includes a first suction port 14a and a second suction port 14b (suction port 14) for introducing air from the external space (indoor space) to be dehumidified into the inside of the housing 20; An outlet 21 for blowing air into the space is formed. The housing 20 has a back surface 20a and a front surface 20b. A first suction port 14a and a second suction port 14b are provided on the back surface 20a. In the back surface 20a, the first suction port 14a is configured to suck air into the first air passage 11a. On the back surface 20a, the second suction port 14b is configured to suck air into the second air passage 11b.

  The first suction port 14a is disposed upstream of the air inlet of the evaporator 5 in the first air passage 11a in the direction of air flow in the first air passage 11a. The second suction port 14b is disposed upstream of the air inlet of the third condensing portion 3c in the second air passage 11b in the air flow direction of the second air passage 11b.

  Note that, in the dehumidifying device 1, in the first air passage 11a, an optional refrigerant circuit that constitutes a refrigerant circuit in addition to the second condenser 3b, the third condenser 3c, and the evaporator 5 disposed in the second air passage 11b. May be arranged. For example, the pressure reducing device 4 may be disposed in the first air passage 11a.

  The housing 20 includes a second partition 13 that partitions the first area 22 and the second area 23. Each of the first area 22 and the second area 23 is defined by the housing 20 and the second partition 13. That is, two regions of the first region 22 and the second region 23 are provided inside the housing 20. In the first region 22, a first air passage 11a and a second air passage 11b partitioned by the first partition 12 are arranged. That is, in the first region 22, the first condenser 3a, the second condenser 3b, and the evaporator 5 arranged in the first air passage 11a are arranged. In the first region 22, a third condenser 3c disposed in the second air passage 11b is disposed. The blower 6 is arranged in the second area 23.

  Referring to FIG. 2 and FIG. 3, second partition 13 has opening 13 a connecting first region 22 and second region 23. The second partition 13 is formed in, for example, a flat plate shape. When the opening 13a of the second partition 13 is viewed from the first region 22 along the direction in which the shaft 6a of the blower 6 extends, the fan 6b is arranged in the opening 13a. The outer diameter D1 of the fan 6b is smaller than the inner diameter D2 of the opening 13a. The second partition 13 is configured so as not to block the suction area of the fan 6b. The height of the second partition 13 is adjusted so that air flowing from the first region 22 to the second region 23 passes through the upper end of the third condenser 3c. Therefore, since heat exchange is performed up to the upper end of the third condenser 3c, heat exchange of the third condenser 3c is not hindered.

  Next, the operation of the dehumidifier 1 during the dehumidifying operation will be described with reference to FIGS. 1, 2 and 4. FIG. 4 is a graph showing a temperature change between the refrigerant and the air in the condenser 3 of the dehumidifier 1. The vertical axis in FIG. 4 indicates the temperature of the refrigerant and the air, and the horizontal axis indicates the position of the flow path of the refrigerant and the air. The circles in FIG. 4 indicate the refrigerant, and the triangles indicate the air. Reference numerals c to f, x2, and y2 in FIG. 4 correspond to the positions of the same reference numerals in FIG. Reference sign c indicates an air inlet of the first condenser 3a. Symbol d indicates an air inlet of the second condenser 3b (air outlet of the first condenser 3a). The symbol e indicates an air outlet of the second condenser 3b. Symbol f indicates an air inlet of the third condenser 3c. Symbol g indicates an air outlet of the third condenser 3c. Reference sign x2 indicates a refrigerant inlet of the condenser 3. The symbol y2 indicates a refrigerant outlet of the condenser 3.

  The refrigerant in a superheated gas state discharged from the compressor 2 flows into the third condensing section 3c arranged in the second air passage 11b. The superheated gas at the temperature T1 flowing into the third condenser 3c is cooled by heat exchange with the air at the temperature T6 taken into the first air passage 11a from the external space through the second suction port 14b. As a result, the refrigerant becomes a gas-liquid two-phase refrigerant having a condensation temperature T2 (39 ° C. in FIG. 4). The condensation temperature T2 is equal to or higher than the temperature T6.

  On the other hand, the air at the temperature T6 taken into the second air passage 11b is heated by exchanging heat with the refrigerant in a superheated gas state having a temperature higher than the temperature T2 and equal to or lower than the temperature T1 in the third condenser 3c. Thus, the temperature T7 (50 ° C. in FIG. 4) of the air that has passed through the third condensing portion 3c of the second air passage 11b can be equal to or higher than the condensing temperature T2 of the refrigerant.

  The refrigerant in the gas-liquid two-phase state at the temperature T2 flowing out of the third condenser 3c flows into the second condenser 3b disposed in the first air passage 11a. The refrigerant in the gas-liquid two-phase state at the temperature T2 that has flowed into the second condenser 3b is exchanged with the air at the temperature T8 that has passed through the first condenser 3a. The gas-liquid two-phase refrigerant flowing out of the second condenser 3b flows into the first condenser 3a disposed in the second air passage 11b. The refrigerant that has flowed into the first condensing section 3a is further cooled by heat exchange with the air at the temperature T4 that has passed through the evaporator 5 in the second air passage 11b, and becomes a supercooled liquid state refrigerant at the temperature T3. . The supercooled liquid state refrigerant flowing out of the first condensing section 3a is decompressed by passing through the decompression device 4, becomes a gas-liquid two-phase state refrigerant, and then evaporates in the second air passage 11b. It flows into the vessel 5. The refrigerant in the gas-liquid two-phase state that has flowed into the evaporator 5 is heated by being exchanged with the air taken into the second air passage 11b from the external space through the first suction port 14a, and is heated to form a superheated refrigerant. Becomes

  On the other hand, the air taken into the second air passage 11b is first dehumidified by being cooled in the evaporator 5 to a temperature T4 lower than the dew point of the air. The cooled and dehumidified air is heated to the temperature T8 by exchanging heat with the refrigerant in the supercooled liquid state in the first condenser 3a. The air at the temperature T8, which has been heat-exchanged with the refrigerant in the supercooled liquid state in the first condensing section 3a, is heated to the temperature T5 by exchanging heat with the refrigerant in the gas-liquid two-phase state in the second condensing section 3b.

  Thus, the temperature T5 of the air that has passed through the second air passage 11b may be higher than the dew point of the air and equal to or lower than the condensation temperature of the refrigerant. The temperature T5 and the temperature T7 are set so that the air passing through the first air passage 11a and the air passing through the second air passage 11b do not lower the air temperature in the external space.

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

  Referring to FIG. 5, a dehumidifier 1 of a comparative example includes a refrigerant circuit 10 in which refrigerant flows sequentially through compressor 2, condenser 3, decompression device 4, and evaporator 5, and a housing that houses refrigerant circuit 10 therein. And In the dehumidifier 1 of the comparative example, only the air passage through which the air taken in passes through the evaporator 5 and the condenser 3 in order is formed. FIG. 6 is a graph showing a temperature change between the refrigerant and the air in the condenser 3 of the dehumidifier 1 of the comparative example. The vertical axis in FIG. 6 indicates the temperature of the refrigerant and the air, and the horizontal axis indicates the position of the flow path of the refrigerant and the air. The circles in FIG. 6 indicate the refrigerant, and the triangles indicate the air. The symbols a, b, x1, and y1 in FIG. 6 correspond to the positions of the same symbols in FIG. Symbol a indicates the air inlet of the condenser 3. Reference sign b indicates an air outlet of the condenser 3. Reference sign x1 indicates a refrigerant inlet of the condenser 3. Reference symbol y1 indicates a refrigerant outlet of the condenser 3.

  With reference to FIGS. 5 and 6, in the dehumidifier 1 of the comparative example, the refrigerant in the superheated gas state discharged from the compressor 2 flows into the condenser 3. The refrigerant in the superheated gas state at the temperature T1 that has flowed into the condenser 3 is taken into the dehumidifier 1 from the external space, and is cooled by being exchanged with the air at the temperature T12 that is cooled when passing through the evaporator 5. Is done. The refrigerant enters a gas-liquid two-phase state at a condensation temperature T10 (44 ° C. in FIG. 6), 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 the temperature T12 exchanges heat with the refrigerant in the superheated gas state at a temperature higher than the temperature T10 and equal to or lower than the temperature T1, the gas-liquid two-phase refrigerant at the temperature T10, or the supercooled liquid state at the temperature T11. Heating. Specifically, the air at the temperature T12 is heated up to the temperature T20 by performing heat exchange with the refrigerant in the supercooled liquid state at the temperature T11 or the refrigerant in the gas-liquid two-phase state at the temperature T10 in the condenser 3. The condenser 3 is heated to a temperature T13 by performing heat exchange with a refrigerant in a superheated gas state having a temperature higher than the temperature T10 and equal to or lower than the temperature T1. Thereby, the temperature T13 of the air that has passed through the evaporator 5 and the condenser 3 in order can be equal to or higher than the condensation temperature T10 of the refrigerant. The temperature T13 is set so as to be substantially equal to the temperature of the external space of the dehumidifier 1. Therefore, in the dehumidifier 1 of the comparative example, when the condensation temperature T10 of the refrigerant is reduced, the temperature T13 of the air passing through the condenser 3 is also reduced. In the dehumidifier 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 is 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.

  On the other hand, in the dehumidifier 1 of the present embodiment, the refrigerant in the superheated gas state in the third condenser 3c and the air at the temperature T6 lower than the air at the temperature T5 that has passed through the second condenser 3b. Heat exchange takes place between them. For this reason, even if the condensation temperature T2 of the refrigerant is reduced, the decrease in the temperature T7 of the air that has passed through the third condensation section 3c is suppressed. Therefore, according to the dehumidifying apparatus 1 of the present embodiment, if the set temperature during the dehumidifying operation is assumed to be equal to that of the dehumidifying apparatus 1 of the comparative example, the dehumidifying apparatus 1 is in the two-phase state of the condensation temperature T2 and the condensation temperature T2. The difference between the maximum value T20 of the temperature of the air exchanged with the refrigerant and the maximum value T20 of the temperature of the air exchanged with the refrigerant in the gas-liquid two-phase state of the condensation temperature T10 and the condensation temperature T10 is calculated. Can also be increased. Therefore, in the dehumidifier 1 of the present embodiment, even if the condensing temperature T2 is lowered, the difference between the condensing temperature T2 and the temperature T20 can be equal to or greater than the dehumidifying device 1 of the comparative example. Since the condensation temperature T2 can be lower than that of the example dehumidifier 1, the EF value can be increased.

  That is, according to the dehumidifier 1 of the present embodiment, heat exchange between the refrigerant in the superheated gas state and the air that has not passed through the evaporator 5 in the third condensing section 3c in the first air passage 11a. Is performed. Therefore, the temperature of the air discharged from the dehumidifier 1 is reduced as compared with the dehumidifier 1 of the comparative example in which heat exchange is performed between the refrigerant in the superheated gas state and the air passing through the evaporator 5 in the condenser 3. Without this, the condensation temperature of the refrigerant can be reduced. As a result, compared to the dehumidifier 1 of the comparative example, the condensation temperature can be reduced and the difference between the condensation pressure and the evaporation pressure can be reduced. Therefore, the EF value indicating the dehumidifying performance can be increased.

  In the second condenser section 3b, heat exchange is performed between the refrigerant in a supercooled liquid state and the air that has passed through the evaporator 5. Therefore, compared to the dehumidifier 1 in which heat exchange is performed between the refrigerant in the supercooled liquid state and the air not passing through the evaporator 5 in the condenser 3, the degree of subcooling can be sufficiently obtained. Therefore, a large amount of dehumidification can be obtained. As a result, in the dehumidifying device 1 of the present embodiment, the EF value indicating the dehumidifying performance increases.

  Furthermore, when the opening 13a of the second partition 13 is viewed from the first region 22 along the direction in which the shaft 6a of the blower 6 extends, the fan 6b is arranged in the opening 13a. Therefore, since the flow of air from the first region 22 to the second region 23 is hardly hindered by the second partition 13, the ventilation resistance can be reduced. Thereby, since the air volume of the blower required to obtain a desired dehumidification amount can be reduced, the input (power consumption) of the blower can be reduced. Therefore, the EF value indicating the dehumidifying performance can be sufficiently increased.

Next, a modified example of the present embodiment will be described.
Modification 1 of the present embodiment will be described with reference to FIG. In the first modification of the present embodiment, the second condenser 3b and the third condenser 3c are integrally formed. That is, the second condenser 3b and the third condenser 3c are not separated from each other via the pipe. On the other hand, the first condenser 3a and the second condenser 3b are separated from each other via a pipe.

  According to the first modification of the first embodiment, since the second condenser 3b and the third condenser 3c are integrally formed, the configuration of the condenser 3 can be simplified. Further, since the second condenser 3b and the third condenser 3c are integrally formed, the manufacture of the condenser 3 is facilitated.

  Next, a second modification of the present embodiment will be described with reference to FIGS. 8 and 9. In the second modification of the present embodiment, the second region 23 extends along the direction in which the shaft 6 a of the blower 6 extends. When the opening 13a of the second partition 13 is viewed from above, the upper end and the lower end of the condenser 3 are arranged in the opening 13a. The vertical height D3 of the condenser 3 is smaller than the inner diameter D2 of the opening 13a.

  According to the second modification of the present embodiment, when the opening 13a of the second partition 13 is viewed from the second region 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 arranged in the opening 13a. Therefore, since the flow of air from the first region 22 to the second region 23 is hardly hindered by the condenser 3 in the vertical direction of the condenser 3, the ventilation resistance can be reduced.

  Further, a third modification of the present embodiment will be described with reference to FIG. In the third modification of the present embodiment, when the opening 13a of the second partition 13 is viewed from the second region 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 open. The left and right ends of the condenser 3 are disposed in the opening 13a. The vertical height D3 of the condenser 3 is smaller than the inner diameter D2 of the opening 13a. The dimension D4 of the width of the condenser 3 in the left-right direction is smaller than the inner diameter D2 of the opening 13a.

  According to the third modification of the present embodiment, when the opening 13a of the second partition 13 is viewed from the second region 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 arranged in the opening 13a, and both ends of the condenser 3 in the left-right direction are arranged in the opening 13a. Therefore, the flow of air from the first region 22 to the second region 23 is hardly hindered by the condenser 3 in the vertical and horizontal directions of the condenser 3, so that the ventilation resistance can be further reduced.

Embodiment 2 FIG.
The dehumidifier 1 according to Embodiment 2 has the structure shown in FIG. FIG. 11 is a diagram showing the heights of the condenser 3 and the evaporator 5. FIG. 12 is a diagram illustrating the widths of the condenser 3 and the evaporator 5.

  Referring to FIGS. 11 and 12, in dehumidifying apparatus 1 according to Embodiment 2, condenser 3 has an evaporator in a direction between evaporator 5 and blower 6 and in a direction from evaporator 5 toward blower 6. When they are arranged so as to overlap with the evaporator 5, they protrude outside the evaporator 5.

  Specifically, the second condenser 3b and the third condenser 3c are arranged at the most downstream in the direction of air flow. The evaporator 5 is arranged at the uppermost stream in the direction of air flow. The first condenser 3a is arranged between the second condenser 3b and the third condenser 3c and the evaporator 5 in the air flow direction. That is, the evaporator 5 is arranged upstream of the first condenser 3a, the second condenser 3b, and the third condenser 3c.

  The sum of the height h2 of the second condenser 3b and the height h3 of the third condenser 3c is larger 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 second condenser 3b. The height of the first condenser 3a is equal to the height h1 of the evaporator 5 and the height h2 of the second condenser 3b. In the height direction of the condenser 3, the third condensing part 3 c projects above the evaporator 5.

  The width w2 of the second condenser 3b is larger 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 first condensing section 3a. The width of the third condensing section 3c is equal to the width w2 of the second condensing section 3b. In the width direction of the condenser 3, the second condenser 3 b and the third condenser 3 c project rightward and leftward from the evaporator 5.

  According to the dehumidifier 1 of the present embodiment, when the condenser 3 is disposed so as to overlap the evaporator 5 in the direction between the evaporator 5 and the blower 6 and between the evaporator 5 and the blower 6. In addition, it protrudes outside the evaporator 5. For this reason, the air can flow to the condenser 3 without being obstructed by the evaporator 5 in the flow direction of the air from the evaporator 5 to the blower 6. Therefore, the configuration of the air path becomes easy.

  When at least one of the upper part and the lower part of the condenser 3 extends beyond the evaporator 5, the second air path 11b of the second air passage 11b that takes in air from the room into at least one of the upper part and the lower part of the condenser 3 The suction port 14b can be arranged on the back surface 20a of the housing 20. When the condenser 3 extends beyond the evaporator 5 in the width direction (lateral direction) of the condenser 3, that is, when the width of the condenser 3 is larger than the width of the evaporator 5, the left side of the condenser 3 is The second suction port 14b of the second air passage 11b that takes in air from the room into at least one of the right side and the right side can be disposed on the back surface 20a of the housing 20. Therefore, the dehumidifier 1 of the present embodiment can be configured without largely changing the configuration of the conventional dehumidifier.

  Further, the heat exchange efficiency can be improved by arranging the second suction port 14b of the second air passage 11b in accordance with the refrigerant inlet of the condenser 3. That is, when the flow of the refrigerant in the condenser 3 arranged at the most downstream of the second air passage 11b is in the vertical direction, the inlet of the high-temperature refrigerant is arranged above the condenser 3. For this reason, the heat exchange efficiency can be improved by arranging the second air passage 11b in accordance with the upper part of the condenser 3. Further, when the refrigerant in the condenser 3 arranged at the most downstream of the second air passage 11b flows from right to left, an inlet for the high-temperature refrigerant is arranged on the right side of the condenser 3. For this reason, the heat exchange efficiency can be improved by arranging the second air passage 11b along the right side of the condenser 3.

Embodiment 3 FIG.
Referring to FIG. 13, in dehumidifying apparatus 1 according to Embodiment 3, first condensing section 3a is arranged between evaporator 5 and second condensing section 3b. The interval t2 between the first condenser 3a and the second condenser 3b is larger than the interval t1 between the first condenser 3a and the evaporator 5. That is, the interval t2 between the first condenser 3a and the second condenser 3b in the direction of air flow from the evaporator 5 to the blower 6 is larger than the interval t1 between the first condenser 3a and the evaporator 5. In addition, the interval between the first condenser 3a and the third condenser 3c in the direction of air flow from the evaporator 5 to the blower 6 is equal to the distance t2 between the first condenser 3a and the second condenser 3b.

  Between the evaporator 5 and the first condenser 3a, air having a temperature (for example, 13 ° C.) lower than room temperature (for example, 27 ° C.) that has exchanged heat with the refrigerant in the evaporator 5 flows to the first condenser 3a. Between the first condensing section 3a and the second condensing section 3b, air having a temperature (for example, 28 ° C.) higher than room temperature (for example, 27 ° C.) that has exchanged heat with the refrigerant in the first condensing section 3a is supplied to the second condensing section 3b. Flows to

  Between the evaporator 5 and the first condenser 3a, when the air passing through the evaporator 5 and the indoor air are mixed, the difference between the condensing temperature and the air temperature becomes smaller, so that the condenser capacity is reduced. The distance t1 between the evaporator 5 and the first condenser 3a may be small. On the other hand, between the first condenser 3a and the second condenser 3b, the air after passing through the first condenser 3a is increased by increasing the interval t2 between the first condenser 3a and the second condenser 3b. A mixing area with outdoor air is provided. Thereby, the difference between the condensation temperature of the second condensation section 3b and the air temperature increases, so that the condensation capacity can be improved.

  According to the dehumidifier 1 of the present embodiment, the interval t2 between the first condenser 3a and the second condenser 3b is larger than the interval t1 between the first condenser 3a and the evaporator 5. Therefore, the difference between the condensing temperature of the first condensing unit 3a and the air temperature is suppressed between the first condensing unit 3a and the evaporator 5 by suppressing the mixing of the air passing through the evaporator 5 and the indoor air. It is possible to suppress the size from becoming smaller. As a result, it is possible to suppress a decrease in the condensation capacity. Further, between the first condensing section 3a and the second condensing section 3b, the mixing between the air passing through the first condensing section 3a and the indoor air is promoted, so that the condensing temperature and the air temperature of the second condensing section 3b are reduced. Can be increased. Thereby, the condensing ability can be improved. Further, since it is possible to provide a run-up area for the air passing through the first condensing section 3a and the second condensing section 3b, the wind speed distribution of the air passing through the second condensing section 3b can be made uniform.

Embodiment 4 FIG.
Referring to FIGS. 14 and 15, in the dehumidifying apparatus 1 according to the fourth embodiment, the air inlets to the second condensing section 3 b and the third condensing section 3 c arranged at the most downstream of the air flow have rear surfaces. 20a and the side surface 20c.

  The third suction port 15 is provided on a side surface 20 c of the housing 20. In the side surface 20c, the third suction port 15 is configured to suck air into the first air passage 11a and the second air passage 11b. The third suction port 15 is configured to suck indoor air between the first condenser section 3a and the second condenser section 3b in the first air passage 11a. The third suction port 15 is configured to suck indoor air between the second suction port 14b and the third condenser 3c in the second air passage 11b.

  Further, in the dehumidifying device 1 of the present embodiment, the interval t2 between the first condenser 3a and the second condenser 3b is equal to the distance between the first condenser 3a and the evaporator 5, as in the above-described third embodiment. It may be larger than the interval t1.

  According to the dehumidifying apparatus 1 of the present embodiment, in addition to the first suction port 14a and the second suction port 14b, the third suction port that sucks air into the first air passage 11a and the second air passage 11b in the housing 20. Since 15 is provided, the air volume of the air passing through the second condensing section 3b and the third condensing section 3c can be increased. Thereby, the condensing ability can be improved.

  In addition, since the first suction port 14a, the second suction port 14b, and the third suction port 15 can be easily formed by providing an opening in the housing 20, the configuration of the conventional dehumidifier can be significantly changed. Instead, the dehumidifier 1 of the present embodiment can be commercialized.

Next, a dehumidifier 1 according to a modification of the fourth embodiment will be described.
Referring to FIG. 16, a dehumidifier 1 according to a modification of the fourth embodiment has a third partition for separating air passing through a supercooling section of first condenser 3a through which a refrigerant in a supercooled liquid state flows. A section 16 is provided. The third partition 16 is disposed between the first condenser 3a and the second condenser 3b so as to close the space between the first condenser 3a and the second condenser 3b. The third suction port 15 is provided above the third partition 16.

  According to the dehumidifying apparatus 1 according to the modification of the fourth embodiment, the third partitioning section 16 performs the heat exchange with the refrigerant in the supercooling section of the first condensing section 3a, the air having a temperature lower than the room temperature, and the indoor air. Is suppressed, so that the condensing ability can be further improved.

Embodiment 5 FIG.
The dehumidifier 1 according to Embodiment 5 has the structure shown in FIG. In the dehumidifier 1 according to Embodiment 5, the refrigerant inlet x2 of the condenser 3 is arranged above the condenser 3, and the refrigerant outlet y2 of the condenser 3 is arranged below the condenser 3. The refrigerant inlet x2 of the condenser 3 is arranged at the most downstream of the air flow, and the refrigerant outlet y2 of the condenser 3 is arranged at the most upstream of the air flow. That is, the refrigerant inlet x2 of the condenser 3 is provided in the third condenser 3c, and the refrigerant outlet y2 of the condenser 3 is provided in the first condenser 3a. The refrigerant inlet z of the evaporator 5 is arranged below the evaporator 5.

  According to the dehumidifier of the present embodiment, the refrigerant flows through the third condenser 3c, the second condenser 3b, and the first condenser 3a in this order. Therefore, the refrigerant flowing through the third condenser 3c flows opposite to the air flowing through the second air passage 11b. The refrigerant flowing through the second condenser 3b and the first condenser 3a flows opposite to the air flowing through the first air passage 11a and the air flowing through the second air passage 11b. Thereby, heat exchange with high temperature efficiency becomes possible, and condensing efficiency can be improved.

  Further, since the inlet of the refrigerant is provided in the third condensing section 3c arranged in the second air passage 11b, the refrigerant having the highest temperature in the condenser 3 is supplied to the room temperature air flowing through the second air passage 11b. And heat exchange can be performed. Thereby, heat exchange performance is improved.

  Further, since the refrigerant outlet y2 of the condenser 3 is disposed below the condenser 3, it is easy to connect the refrigerant outlet y2 of the condenser 3 to the refrigerant inlet z disposed below the evaporator 5. Becomes Further, since the refrigerant outlet y2 of the condenser 3 is provided in the first condenser section 3a, the pipe connecting the first condenser section 3a and the evaporator 5 can be shortened. In addition, the refrigerant flowing through the evaporator 5 and the air flowing through the first air passage 11a can be made to face each other. Thereby, the evaporation ability can be improved. Further, generally, the refrigerant flowing through the evaporator 5 flows from the bottom to the top due to the stability of the flow. According to the arrangement of the condenser 3 and the evaporator 5 in the present embodiment, it is possible to flow the refrigerant from the bottom to the top in the evaporator 5.

Embodiment 6 FIG.
Referring to FIG. 17, in the dehumidifying apparatus 1 according to Embodiment 6, the distribution numbers of the second condenser section 3b and the third condenser section 3c are larger than the distribution number of the first condenser section 3a. In other words, the number of heat transfer tubes through which the refrigerant of each of the second condenser 3b and the third condenser 3c flows is greater than the number of heat transfer tubes through which the refrigerant of the first condenser 3a flows.

  In addition, as shown in FIG. 17, you may change the distribution number for every 1st condensation part 3a, 2nd condensation part 3b, and 3rd condensation part 3c. Referring to FIG. 18, the number of distributions may be reduced in the middle of first condensing section 3a.

  According to the dehumidifying device 1 of the present embodiment, the distribution numbers of the second condenser 3b and the third condenser 3c are larger than the distribution number of the first condenser 3a. Therefore, the pressure loss can be reduced by reducing the flow rate of the refrigerant in a region where the pressure loss is large because the flow rate of the refrigerant is high in the superheated gas state or the gas-liquid two-phase state. On the other hand, since the flow rate of the refrigerant is low when the refrigerant is in the supercooled liquid state, heat exchange with high efficiency can be performed by increasing the flow rate of the refrigerant in a region where the pressure loss is small.

Embodiment 7 FIG.
Referring to FIG. 19, in dehumidifying device 1 according to Embodiment 7, third condensing portion 3c is configured to extend in second air passage 11b on the side opposite to blower 6 with respect to second partition portion 13. Have been.

  Since the first condenser 3a, the second condenser 3b, and the evaporator 5 are arranged in the second air passage 11b, the pressure loss of the air flowing through the second air passage 11b is reduced by the pressure loss of the air flowing through the first air passage 11a. It becomes smaller than the pressure loss. Therefore, the amount of air flowing through the first air passage 11a decreases due to an increase in the amount of air flowing through the second air passage 11b. Therefore, the amount of air flowing through the evaporator 5 disposed in the first air passage 11a decreases, and the amount of dehumidification decreases. For example, if the total number of rows and the number of fins of the evaporator 5, the first condenser 3a and the second condenser is equal to the number of rows and the number of fins of the third condenser 3c, the same ventilation resistance is obtained at the same front area. become. Therefore, the flow rate of the air flowing through the first air passage 11a and the second air passage 11b can be easily determined by the ratio of the front area of the evaporator 5, the first condenser section 3a and the second condenser section 3b to the front area of the third condenser section. Can be adjusted.

  According to the dehumidifier 1 of the present embodiment, the third condenser 3c is configured to extend in the second air passage 11b on the side opposite to the blower 6 with respect to the second partition 13. For this reason, the pressure loss of the second air passage 11b can be increased. In the first air passage 11a, since the first condenser 3a, the second condenser 3b, and the evaporator 5 are disposed, the pressure loss increases. Therefore, by increasing the pressure loss in the second air passage 11b, The drift of air into the two air passages 11b can be suppressed. Thereby, a decrease in the amount of dehumidification in the evaporator 5 can be suppressed. For this reason, a highly efficient dehumidifier 1 can be obtained.

Embodiment 8 FIG.
Referring to FIG. 20, in a dehumidifying apparatus 1 according to Embodiment 8, the refrigerant circuit 10 is configured to flow the refrigerant flowing out of the evaporator 5 to the compressor 2 via the condenser 3. In the dehumidifier 1 of the present embodiment, the condenser 3 includes the high-low pressure heat exchange unit 17. The high-low pressure heat exchange section 17 is a first flow path connecting the refrigerant outlet of the first condenser section 3a and the refrigerant inlet of the pressure reducing device 4, the refrigerant outlet of the evaporator 5, and the suction port (refrigerant inlet) of the compressor 2. And a second flow path for connecting

  In the high / low pressure heat exchange section 17, heat exchange is performed between the refrigerant flowing through the first flow path and the refrigerant flowing through the second 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 increasing the enthalpy difference of the refrigerant flowing through the evaporator 5.

  Further, the suction port (refrigerant inlet) of the compressor 2 needs to suck the refrigerant gasified in the evaporator 5 in order to maintain reliability. However, in the evaporator 5, the gas portion of the refrigerant locally becomes high in temperature, thereby deteriorating the heat exchange performance.

  In the refrigerant circuit 10 of the present embodiment, even if the refrigerant flowing out of the evaporator 5 is in a gas-liquid two-phase state, the gasified refrigerant can be returned to the refrigerant inlet of the compressor 2. For this reason, the performance of the evaporator 5 does not decrease, and the reliability of the compressor 2 is not impaired. Further, even if the distribution of the refrigerant in the evaporator 5 is poor, the refrigerant in the gas-liquid two-phase state can flow to the evaporator 5, so that the performance of the evaporator 5 can be maximized.

  As described above, according to the dehumidifier 1 of the present embodiment, the refrigerant circuit 10 is configured to flow the refrigerant flowing out of the evaporator 5 to the compressor 2 via the condenser 3. For this reason, it becomes possible to supply the liquid refrigerant to a region where the heat exchange efficiency is reduced in the evaporator 5 due to generation of a superheated gas. Thereby, the heat exchange performance of the evaporator 5 can be improved.

  The embodiments disclosed this time are to be considered in all respects as illustrative and not restrictive. The scope of the present invention is defined by the terms of the claims, rather than the description above, and is intended to include any modifications within the scope and meaning equivalent to the terms of the claims.

  Reference Signs List 1 dehumidifier, 2 compressor, 3 condenser, 3a first condenser, 3b second condenser, 3c third condenser, 4 decompressor, 5 evaporator, 6 blower, 6a shaft, 6b fan, 10 refrigerant circuit , 11a first air path, 11b second air path, 12 first partition, 13 second partition, 13a opening, 14a first inlet, 14b second inlet, 15 third inlet, 16 third Partition part, 17 high and low pressure heat exchange part, 20 housing, 20a back surface, 20b front surface, 20c side surface, 21 outlet, 22 first area, 23 second area.

Claims (8)

A housing,
A compressor housed inside the housing, a condenser, a refrigerant circuit including a decompression device and an evaporator,
A fan having a fan that rotates about an axis, and a blower housed inside the housing,
In the refrigerant circuit, the refrigerant flows through the compressor, the condenser, the pressure reducing device, and the evaporator in order,
The condenser includes a first condenser in which the refrigerant in a supercooled liquid state flows, a second condenser in which the refrigerant in a gas-liquid two-phase state flows, and a third condenser in which the refrigerant in a superheated gas state flows. Including
The housing is
A first air passage through which the air taken in from the outside of the housing by rotation of the fan around the axis passes through the evaporator, the first condenser, and the second condenser in order; A first partition unit that partitions a second air passage through which the air taken in from the outside of the housing to the inside by the fan rotating about the axis passes through the third condensing unit;
An opening that connects a first region in which the first air passage and the second air passage divided by the first partition portion are arranged and a second region in which the blower is arranged; A second partition section for partitioning the area and the second area,
The dehumidifier according to claim 1, wherein the fan is disposed in the opening when the opening of the second partition is viewed from the first region along the direction in which the axis extends.   When the condenser is disposed between the evaporator and the blower and overlaps with the evaporator in a direction from the evaporator to the blower, the condenser projects outward from the evaporator. The dehumidifier according to claim 1. The first condensing unit is disposed between the evaporator and the second condensing unit,
The dehumidifier according to claim 1, wherein an interval between the first condenser and the second condenser is larger than an interval between the first condenser and the evaporator. The housing includes a back surface provided with a first suction port and a second suction port, and a side surface provided with a third suction port,
On the back surface, the first suction port is configured to suck air into the first air passage, and the second suction port is configured to suck air into the second air passage,
The third suction port on the side surface is configured to suck air into the first air passage and the second air passage,
The said 3rd suction port is comprised so that air may be sucked between the said 1st condensing part and the said 2nd condensing part in the said 1st air path. Dehumidifier. In the condenser, the refrigerant sequentially flows through the third condenser, the second condenser, and the first condenser,
The refrigerant inlet is disposed above the condenser, and is provided in the third condenser,
The dehumidifier according to any one of claims 1 to 4, wherein the outlet of the refrigerant is arranged below the condenser and is provided in the first condenser.   The dehumidifier according to any one of claims 1 to 5, wherein a distribution number of each of the second condensation section and the third condensation section is larger than a distribution number of the first condensation section.   The dehumidifier according to any one of claims 1 to 6, wherein the third condensing unit is configured to extend in the second air passage on a side opposite to the blower with respect to the second partition unit. apparatus.   The dehumidifier according to any one of claims 1 to 7, wherein the refrigerant circuit is configured to flow the refrigerant flowing out of the evaporator to the compressor via the condenser.

Images