TWI671494B - Dehumidifier - Google Patents

Abstract

The dehumidifying device (1) includes a frame body (20), a refrigerant circuit (10), and a blower (6). The condenser (3) includes: a first condenser (3a), a refrigerant flow in a supercooled liquid state; a second condenser (3b), a refrigerant flow in a gas-liquid two-phase state; and a third condenser (3c) ), The refrigerant flows in the superheated gas state. The first partition (12) partitions the first air path (11a) from the second air path (11b). The second partition (13) has an opening (13a) that connects the first region (22) and the second region (23). When the opening (13a) of the second partition (13) is viewed from the first area (22) along the direction in which the shaft (6a) extends, the fan (6b) is arranged in the opening (13a). .

Description

Dehumidifier

The present invention relates to a dehumidifying device, and more particularly, to a dehumidifying device including a refrigerant circuit.

In the conventional dehumidifier including a refrigerant circuit, an evaporator and a condenser are arranged in parallel. The evaporator is located upstream of the condenser by the flow of air generated by the blower. In the conventional dehumidifier, the air taken in the dehumidifier was cooled and dehumidified in the evaporator, and the condenser cooled the dehumidified air in the evaporator.

As an index indicating the dehumidification performance of a dehumidification device, an EF (Energy Factor) value (L / kWh) indicating a dehumidification amount L per 1 kWh is known. The higher the EF value of the dehumidifier, the more power consumption can be reduced. As a method for increasing the EF value of the dehumidifier, it is thought to reduce the condensation temperature of the refrigerant so that the difference between the condensation pressure and the evaporation pressure becomes smaller, thereby reducing the load on the compressor.

Furthermore, in Japanese Patent Application Laid-Open No. 5-87417 (Patent Document 1), a dehumidifying device is disclosed in which a part of a condenser is disposed in an air path of air that is heat-exchanged in an evaporator, and the condenser The remainder is placed in the air path of the air that has not undergone heat exchange in the evaporator.

[Leading Patent Literature] [Patent Literature]

[Patent Document 1] Japanese Unexamined Patent Publication No. 5-87417

In conventional dehumidifiers, the refrigerant in the superheated gas state of the condenser, the refrigerant in the gas-liquid two-phase state, and the refrigerant in the supercooled liquid state exchange heat with the air subjected to heat exchange in the evaporator. Because the temperature of the air passing through the condenser decreases as the condensation temperature decreases, the difference between the temperature of the air passing through the condenser and the condensation temperature becomes smaller. Therefore, the coagulation temperature cannot be sufficiently reduced. Therefore, it is difficult to sufficiently increase the EF value.

Moreover, in the dehumidifier described in this publication, since the outlet of the refrigerant in the condenser is disposed in the air path of the air that has not been heat-exchanged in the evaporator, the degree of subcooling cannot be sufficiently obtained in the condenser. As a result, it is difficult to sufficiently increase the EF value in the dehumidifier described in this publication because it is difficult to obtain a large amount of dehumidification.

In addition, when the ventilation resistance of the air flowing in the dehumidifying device becomes large, the input (power consumption) of the blower increases because the air volume of the blower required to obtain the desired amount of dehumidification increases. Therefore, it is difficult to sufficiently increase the EF value.

The present invention was developed in view of this problem, and an object thereof is to provide a dehumidifier having a high EF value.

The dehumidification device of the present invention includes a frame, a refrigerant circuit, and a blower. The refrigerant circuit includes a compressor, a condenser, a pressure reducing device, and an evaporator housed inside the casing. The blower is a fan that rotates around a shaft and is housed in the interior of the housing. In the refrigerant circuit, the refrigerant flows through the compressor, condenser, pressure reducing device and evaporator in sequence. The condenser includes: a first condensing portion, which is a refrigerant flow in a supercooled liquid state; a second condensing portion, which is a refrigerant flow in a gas-liquid two-phase state; and a third condensing portion, a refrigerant flow in a superheated gas state. The frame includes a first partition and a second partition. The first partitioning section partitions the first air path from the second air path, and the first air path is rotated by the fan around the shaft, and the air taken in from the outside of the casing sequentially passes through the evaporation. Device, the first condensation part, and the second condensation part, the second air path is rotated by the fan around the shaft, and the air taken in from the outside of the casing passes through the third condensation part. The second partition section has an opening that connects the first air path partitioned by the first partition section, the first region of the second air path, and the second region of the blower, and connects the first The area is separated from the second area. When the opening portion of the second partition portion is viewed from the first region along the direction in which the shaft extends, the fan system is disposed in the opening portion.

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

1‧‧‧ Dehumidifier

2‧‧‧compressor

3‧‧‧ Condenser

3a‧‧‧The first condensation part

3b‧‧‧ 2nd condensation unit

3c‧‧‧3rd condensation unit

4‧‧‧ Buck device

5‧‧‧Evaporator

6‧‧‧ blower

6a‧‧‧axis

6b‧‧‧fan

10‧‧‧Refrigerant circuit

11a‧‧‧The first wind road

11b‧‧‧Second Wind Road

12‧‧‧ the first partition

13‧‧‧ 2nd Division

13a‧‧‧ opening

14a‧‧‧1st suction port

14b‧‧‧Second suction port

15‧‧‧3rd suction port

16‧‧‧ the third partition

17‧‧‧High and low pressure heat exchange department

20‧‧‧Frame

20a‧‧‧Back

20b‧‧‧front

20c‧‧‧side

21‧‧‧ blowing outlet

22‧‧‧Area 1

23‧‧‧ Zone 2

Fig. 1 is a refrigerant circuit diagram of a dehumidifier according to a first embodiment of the present invention.

Fig. 2 is a schematic diagram showing the structure of a dehumidifier according to the first, second, and fifth embodiments of the present invention.

Fig. 3 is a diagram showing a positional relationship between a fan and a second partition portion according to the first embodiment of the present invention.

Fig. 4 is a graph showing changes in the temperature of the refrigerant and air in the condenser of the first embodiment of the present invention.

Fig. 5 is a refrigerant circuit diagram of a dehumidifier according to a comparative example of the first embodiment of the present invention.

Fig. 6 is a graph showing changes in temperature of a refrigerant and air in a condenser of a comparative example of the first embodiment of the present invention.

Fig. 7 is a refrigerant circuit diagram of a dehumidifier according to a first modification of the first embodiment of the present invention.

Fig. 8 is a schematic diagram showing the structure of a dehumidifier according to a second modification of the first embodiment of the present invention.

Fig. 9 is a diagram showing a positional relationship between a fan, a second partition, and a condenser in a second modification of the first embodiment of the present invention.

Fig. 10 is a diagram showing the positional relationship among a fan, a second partition, and a condenser according to a third modification of the first embodiment of the present invention.

Fig. 11 is a diagram showing the positional relationship between the condenser and the evaporator in the height direction of the condenser according to the second embodiment of the present invention.

Fig. 12 is a diagram showing the positional relationship between the condenser and the evaporator in the width direction of the condenser according to the second embodiment of the present invention.

Fig. 13 is a schematic diagram showing the structure of a dehumidifier according to a third embodiment of the present invention.

Fig. 14 is a schematic diagram showing the structure of a dehumidifier according to a fourth embodiment of the present invention.

Fig. 15 is a schematic perspective view showing the structure of a dehumidifier according to a fourth embodiment of the present invention.

Fig. 16 is a schematic diagram showing the structure of a dehumidifier according to a modification of the fourth embodiment of the present invention.

Fig. 17 is a schematic diagram showing the configuration of a condenser according to a sixth embodiment of the present invention.

Fig. 18 is a schematic diagram showing another configuration of a condenser according to a sixth embodiment of the present invention.

Fig. 19 is a schematic diagram showing the structure of a dehumidifier according to a seventh embodiment of the present invention.

Fig. 20 is a refrigerant circuit diagram of a dehumidifier according to an eighth embodiment of the present invention.

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 descriptions thereof are not repeated.

First Embodiment

1 and 2, the dehumidifier 1 according to the first embodiment includes a refrigerant circuit 10 including a compressor 2, a condenser 3, a pressure reducing device 4, and an evaporator 5; a blower 6; and a frame 20, The refrigerant circuit 10 and the blower 6 are housed inside. The condenser 3 and the evaporator 5 are heat exchangers that perform heat exchange between the refrigerant and the air. Each of the condenser 3 and the evaporator 5 has an inlet and an outlet of a refrigerant, and an inlet and an outlet of air. The housing 20 is a dehumidifier 1 that faces external air (indoor space) as a dehumidification target.

The refrigerant circuit 10 of the dehumidifier 1 is housed inside the housing 20 and constitutes a refrigeration cycle. The refrigerant circuit 10 is configured by connecting the compressor 2, the condenser 3, the pressure reducing device 4, and the evaporator 5 in order by piping. As shown by an arrow in FIG. 2, in the refrigerant circuit 10, the refrigerant system flows through the compressor 2, the condenser 3, the pressure reducing device 4, and the evaporator 5 in this order.

Compressor 2 sucks in low-pressure refrigerant, compresses it, and discharges it as high-pressure refrigerant. The compressor 2 is, for example, an inverter compressor with a variable discharge capacity of the refrigerant. The amount of refrigerant circulation 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. Condenser 3 includes: a first condensing portion 3a, which is a refrigerant flow in a supercooled liquid state; a second condensing portion 3b, which is a refrigerant flow in a gas-liquid two-phase state; and a third condensing portion 3c, a refrigerant flow in a superheated gas state . The first condensing portion 3a only needs to have a region through which the refrigerant in the supercooled liquid state flows, and may also have a region through which the refrigerant in the supercooled liquid state and the gas-liquid two-phase state flows. The third condensing portion 3c only needs to have a region through which the refrigerant in a superheated gas state flows, and may also have a region through which the refrigerant in a superheated gas state and a gas-liquid two-phase state flows. In the condenser 3, the refrigerant system flows in sequence through the third condensation part 3c, the second condensation part 3b, and the first condensation part 3a.

Each of the first condensation part 3a, the second condensation part 3b, and the third condensation part 3c has a refrigerant inlet and a refrigerant outlet. The refrigerant inlet of the third condensing portion 3c is connected to the discharge outlet of the compressor 2. The refrigerant inlet of the second condensation part 3b is connected to the refrigerant outlet of the third condensation part 3c. The refrigerant inlet of the first condensation part 3a is connected to the refrigerant outlet of the second condensation part 3b.

The first condensing portion 3a, the second condensing portion 3b, and the third condensing portion 3c may be configured in a single row or a plurality of rows. In this embodiment, the first coagulation part 3a, the second coagulation part 3b, and the third coagulation part 3c are separated from each other via a pipe. In addition, the first coagulation part 3a, the second coagulation part 3b, and the third coagulation part 3c may be integrally formed.

The pressure reducing device 4 depressurizes 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 condensing section 3c.

The evaporator 5 absorbs heat from the refrigerant expanded in the pressure reducing device 4 to 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 pressure reducing device 4. The refrigerant outlet of the evaporator 5 is connected to the suction inlet of the compressor 2. The evaporator 5 is arranged in parallel with the first condensing portion 3a. The evaporator 5 is located upstream of the condenser 3 in the flow of air generated by the fan 6.

The blower 6 is housed inside the housing 20. The blower 6 is configured to take in the air from the outside of the housing 20 into the inside and to send the air to the condenser 3 and the evaporator 5. In the present embodiment, the blower 6 includes a fan 6b that rotates around the shaft 6a. The fan 6b rotates around the axis 6a. As shown by arrows A and C in the figure, the air taken in from the room passes through the condenser 3 and the evaporator 5 and is shown by the arrow B in the figure. It is then discharged indoors. In the present embodiment, the blower 6 is such that the flow of air generated by the blower 6 is located further downstream than the condenser 3. In addition, the air blower 6 is based on the flow of air generated by the air blower 6, and may be disposed between the condenser 3 and the evaporator 5, or may be disposed further upstream than the evaporator 5. The blower 6 series may be one, for example.

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

The space defining the first air passage 11a need not be completely separated from the space defining the second air passage 11b. In the present embodiment, the space of the first air passage 11a is defined as the air flow direction in the first air passage 11a is downstream of the second condensing portion 3b, and is connected to the space of the second air passage 11b.

The direction of air flow in the first air path 11a. One end (upstream end portion) located on the upstream side of the first partition portion 12 is disposed more upstream than the air outlet of the evaporator 5. In the air flow direction in the second air path 11b, the other end (downstream end) located on the downstream side of the first partition section 12 is disposed at the same position as or more than the air outlet of the first condensation section 3a. The exit is further upstream. The first partition 12 is formed in a flat plate shape, for example. The first partition 12 is fixed to the inside of the housing 20.

In the housing 20, a first suction port 14a and a second suction port are formed. 14b (suction port 14) is used to suck air into the inside of the housing 20 from an external space (indoor space) as a dehumidification target; and an air outlet 21 is used to blow air into the external space from the inside. The housing 20 includes a back surface 20a and a front surface 20b. The first suction port 14a and the second suction port 14b are provided on the back surface 20a. On 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 path 11b.

The first suction port 14a is a flow direction of the air in the first air path 11a, and is disposed more upstream than the air inlet of the evaporator 5 in the first air path 11a. The second suction port 14b is a direction in which the air flows in the second air path 11b, and is disposed more upstream than the air inlet of the third condensation part 3c in the second air path 11b.

In addition, in the dehumidifier 1, the first air path 11a may be arranged to constitute a refrigerant in addition to the second condensation part 3b, the third condensation part 3c, and the evaporator 5 disposed in the second air path 11b. Any component of the circuit. For example, the pressure reducing device 4 may be arranged in the first air passage 11a.

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

2 and 3, the 2nd partition part 13 has the opening part 13a which connects the 1st area 22 and the 2nd area 23. The second partition 13 is formed in a flat plate shape, for example. When the opening portion 13a of the second partition portion 13 is viewed from the first region 22 along the direction in which the axis 6a of the blower 6 extends, the fan 6b is disposed inside the opening portion 13a. The outer diameter D1 of the fan 6b is smaller than the inner diameter D2 of the opening portion 13a. The second partition portion 13 is configured not to close the suction area of the fan 6b. In addition, the height of the second partition portion 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 condensation portion 3c. Therefore, since heat exchange is performed to the upper end of the third condensation part 3c, heat exchange of the third condensation part 3c is not hindered.

Next, the operation during the dehumidifying operation of the dehumidifying device 1 will be described with reference to FIGS. 1, 2 and 4. FIG. 4 is a graph showing changes in the temperature of the refrigerant and air in the condenser 3 of the dehumidifier 1. The vertical axis of 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 circle in FIG. 4 indicates the refrigerant, and the triangle indicates air. Symbols c to f, x2, and y2 in FIG. 4 correspond to positions of the same symbols in FIG. 1. The symbol c indicates an air inlet of the first condensation portion 3a. The symbol d indicates the air inlet of the second condensation portion 3b (the air outlet of the first condensation portion 3a). The symbol e indicates an air outlet of the second condensation portion 3b. The symbol f indicates the air inlet of the third condensation part 3c. The symbol g indicates an air outlet of the third condensation portion 3c. The symbol x2 indicates the refrigerant inlet of the condenser 3. The symbol y2 indicates a refrigerant outlet of the condenser 3.

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

On the other hand, the air taken in at the temperature T6 in the second air passage 11b is heated by heat exchange between the third condensing portion 3c and a refrigerant in a superheated gas state exceeding the temperature T2 and below the temperature T1. As a result, the temperature T7 (50 ° C. in FIG. 4) of the air that has passed through the third condensing portion 3c of the second air path 11 b can be equal to or higher than the condensation temperature T2 of the refrigerant.

The refrigerant in a gas-liquid two-phase state at a temperature T2 flowing from the third condensation portion 3c flows into the second condensation portion 3b disposed in the first air passage 11a. The refrigerant flowing into the gas-liquid two-phase state at the temperature T2 of the second condensation section 3b exchanges heat with the air having passed through the temperature T8 of the first condensation section 3a. The gas-liquid two-phase refrigerant flowing out from the second condensation portion 3b flows into the first condensation portion 3a arranged in the first air passage 11a. The refrigerant flowing into the first condensing portion 3a is cooled by heat exchange with the air that has passed through the temperature T4 of the evaporator 5 in the first air path 11a, and becomes a refrigerant in a supercooled liquid state at temperature T3. The refrigerant in the supercooled liquid state flowing from the first condensing portion 3a is depressurized by the pressure reducing device 4 to become a refrigerant in a gas-liquid two-phase state, and then flows into the evaporation disposed in the first air path 11a.器 5。 5. The refrigerant in the gas-liquid two-phase state flowing into the evaporator 5 exchanges heat with the air taken into the first air passage 11a from the external space through the first suction port 14a, and is heated to become a refrigerant in a superheated gas state.

On the other hand, the air taken in the first air path 11a is first dehumidified by the temperature T4 at which the evaporator 5 is cooled below the dew point of the air. The cooled and dehumidified air is heated to a temperature T8 by exchanging heat with a refrigerant in a supercooled liquid state at the first condensation portion 3a. In the first condensation part 3a The air at a temperature T8 that performs heat exchange with the refrigerant in the supercooled liquid state is heated to the temperature T5 by performing heat exchange with the refrigerant in the gas-liquid two-phase state at the second condensation portion 3b.

As a result, the temperature T5 of the air that has passed through the first air path 11a exceeds the dew point of the air, and may become lower than the condensation temperature of the refrigerant. The temperatures T5 and T7 are set such that the temperature of the external space is not lowered by the air that has passed through the first air path 11a and the air that has passed through the second air path 11b.

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

Referring to FIG. 5, the dehumidifying device 1 of the comparative example includes a refrigerant circuit 10 that circulates the refrigerant in the compressor 2, the condenser 3, the pressure reducing device 4, and the evaporator 5 in sequence; and a housing that houses the refrigerant circuit 10. Inside. In the dehumidifying device 1 of the comparative example, only the air taken in the inside thereof passes through the air path of the evaporator 5 and the condenser 3 in this order. FIG. 6 is a graph of temperature changes of the refrigerant and air in the condenser 3 of the dehumidifier 1 of the comparative example. The vertical axis of 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 circle in FIG. 6 indicates the refrigerant, and the triangle indicates air. The symbols a, b, x1, and y1 in FIG. 6 correspond to the positions of the same symbols in FIG. 5. The symbol a indicates the air inlet of the condenser 3. The symbol b indicates an air outlet of the condenser 3. The symbol x1 indicates the refrigerant inlet of the condenser 3. The symbol y1 indicates a refrigerant outlet of the condenser 3.

Referring 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 flowing into the condenser 3 is compared with the temperature T12 which is cooled when taken into the dehumidifier 1 from the external space and passed through the evaporator 5 The air is cooled by heat exchange. The refrigerant system is in 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 coagulation temperature T10 and the temperature T11 are above the temperature T12.

On the other hand, the air at the temperature T12 passes through the condenser 3 and the refrigerant in a superheated gas state exceeding the temperature T10 and below the temperature T1, the gas-liquid two-phase refrigerant in the temperature T10, or the supercooled liquid in the temperature T11. The refrigerant is heated by heat exchange. Specifically, the air at the temperature T12 is heated to the temperature T20 by heat exchange between the condenser 3 and 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. The condenser 3 exchanges heat with a refrigerant in a superheated gas state exceeding the temperature T10 and below the temperature T1, and is heated to a temperature T13. Thereby, the temperature T13 of the air passing through the evaporator 5 and the condenser 3 in this order can become the condensation temperature T10 of the refrigerant or more. The temperature T13 is set to the same degree as the temperature of the outer 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 dehumidifying device 1 of the comparative example, the difference between the condensation temperature T10 and the highest value T20 of the temperature of the air at which the refrigerant in the gas-liquid two-phase state at the condensation temperature T10 performs heat exchange becomes smaller. Therefore, in the dehumidifier 1 of the comparative example, since the condensation temperature T10 cannot be sufficiently lowered, it is difficult to increase the EF value.

In contrast, in the dehumidifier 1 according to this embodiment, heat is generated between the refrigerant in the superheated gas state in the third condensation section 3c and the air at a temperature T6 which is lower than the temperature of the air passing through the temperature T5 of the second condensation section 3b. exchange. Therefore, even if the condensation temperature T2 of the refrigerant is reduced, a decrease in the temperature T7 of the air passing through the third condensation portion 3c is suppressed. Therefore, if the division according to this embodiment is In the humid device 1, if the set temperature during the dehumidification operation is set to be the same as that of the dehumidifier 1 of the comparative example, the refrigerant at the condensation temperature T2 and the condensation temperature T2 in the gas-liquid two-phase state can exchange heat with the air. The difference between the highest temperature T20 is larger than the difference between the highest temperature T20 of the condensation temperature T10 and the highest temperature T20 of the air in which the refrigerant in the gas-liquid two-phase state performs heat exchange. Therefore, in the dehumidifier 1 of this embodiment, even if the condensation temperature T2 is reduced, the difference between the condensation temperature T2 and the highest value T20 can be made equal to or more than the dehumidifier 1 of the comparative example, so the ratio of the condensation temperature T2 can be compared. For example, the dehumidifier 1 is lowered, and the EF value can be increased.

That is, according to the dehumidifier 1 according to this embodiment, heat exchange is performed between the refrigerant in the supercondensed gas state in the third condensation section 3c and the air that has not passed through the evaporator 5 in the second air path 11b. Therefore, compared with the dehumidifier 1 of the comparative example in which heat is exchanged between the refrigerant in the superheated gas state of the condenser 3 and the air passing through the evaporator 5, the temperature of the air coming out of the dehumidifier 1 can be reduced. Lower the condensation temperature of the refrigerant. As a result, as compared with the dehumidifier 1 of the comparative example, the condensation temperature is reduced, and the difference between the condensation pressure and the evaporation pressure can be made small. Therefore, it is possible to increase the EF value indicating dehumidification performance.

In the second condensing portion 3b, heat exchange is performed between the refrigerant in the supercooled liquid state and the air passing through the evaporator 5. Therefore, compared with the dehumidifier 1 that performs heat exchange between the refrigerant in the supercooled liquid state of the condenser 3 and the air that has not passed through the evaporator 5, 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 according to this embodiment, the EF value indicating the dehumidifying performance becomes high.

Furthermore, when the opening portion 13a of the second partition portion 13 is viewed from the first region 22 along the direction in which the axis 6a of the blower 6 extends, the fan 6b is disposed inside the opening portion 13a. Therefore, since the flow of air from the first region 22 to the second region 23 is difficult to be hindered by the second partition 13, the ventilation resistance can be reduced. Therefore, since the air volume of the blower required to obtain the desired amount of dehumidification can be reduced, the input (power consumption) of the blower can be reduced. Therefore, it is possible to sufficiently increase the EF value indicating dehumidification performance.

Next, a modification of this embodiment will be described.

A first modification of this embodiment will be described with reference to FIG. 7. In the first modification of this embodiment, the second coagulation portion 3b and the third coagulation portion 3c are integrally formed. That is, the second coagulation portion 3b and the third coagulation portion 3c are separated from each other without a pipe. On the other hand, the first coagulation part 3a and the second coagulation part 3b are separated from each other via a pipe.

According to the first modification of the first embodiment, since the second coagulation portion 3b and the third coagulation portion 3c are integrally formed, the configuration of the condenser 3 can be simplified. Moreover, since the 2nd coagulation part 3b and the 3rd coagulation part 3c are integrally comprised, manufacture of the condenser 3 becomes easy.

Next, a second modification of this embodiment will be described with reference to FIGS. 8 and 9. In the second modification of this embodiment, when the opening portion 13a of the second partition portion 13 is viewed from the second region 23 along the direction in which the axis 6a of the blower 6 extends, the upper and lower ends of the condenser 3 are arranged. In the opening 13a. The height dimension D3 in the up-down direction of the condenser 3 is smaller than the inner diameter D2 of the opening portion 13a.

According to the second modification of this embodiment, when the opening portion 13a of the second partition portion 13 is viewed from the second region 23 along the direction in which the axis 6a of the blower 6 extends, the upper and lower ends of the condenser 3 are covered. It is arrange | positioned in the opening part 13a. Therefore, since the flow of air from the first region 22 to the second region 23 in the up-down direction of the condenser 3 is hardly obstructed by the condenser 3, the ventilation resistance can be made smaller.

Furthermore, a third modification of this embodiment will be described with reference to FIG. 10. In the third modification of the present embodiment, when the opening portion 13 a of the second partition portion 13 is viewed from the second region 23 along the direction in which the axis 6 a of the blower 6 extends, the upper and lower ends of the condenser 3 are arranged. Both ends in the left-right direction of the condenser 3 are arranged in the opening portion 13a in the opening portion 13a. The height dimension D3 in the up-down direction of the condenser 3 is smaller than the inner diameter D2 of the opening portion 13a. The width dimension D4 in the left-right direction of the condenser 3 is smaller than the inner diameter D2 of the opening portion 13a.

According to the third modification of this embodiment, when the opening portion 13a of the second partition portion 13 is viewed from the second region 23 along the direction in which the axis 6a of the blower 6 extends, the upper and lower ends of the condenser 3 are covered. It is arrange | positioned in the opening part 13a, and both ends of the condenser 3 in the left-right direction are arrange | positioned in the opening part 13a. Therefore, since the flow of air from the first region 22 to the second region 23 in the up-down direction and the left-right direction of the condenser 3 is difficult to be hindered by the condenser 3, the ventilation resistance can be made smaller.

Second embodiment

The dehumidifier 1 according to the second embodiment includes a structure shown in Fig. 2. FIG. 11 is a diagram showing the heights of the condenser 3 and the evaporator 5. FIG. 12 is a diagram showing the widths of the condenser 3 and the evaporator 5.

Referring to FIGS. 11 and 12, in the dehumidifier 1 of the second embodiment, the condenser 3 is located between the evaporator 5 and the blower 6 and is arranged in a direction from the evaporator 5 to the blower 6 so as to be connected to the evaporator. When 5 overlaps, it projects more outward than the evaporator 5.

Specifically, the second condensing portion 3b and the third condensing portion 3c are arranged at the most downstream in the flow direction of the air. The evaporator 5 is arranged at the most upstream of the air flow direction. The first condensation part 3 a is arranged between the second condensation part 3 b and the third condensation part 3 c and the evaporator 5 in the air flow direction. That is, the evaporator 5 is arranged further upstream than the first condensation part 3a, the second condensation part 3b, and the third condensation part 3c.

The sum of the height h2 of the second condensation part 3b and the height h3 of the third condensation part 3c is larger than the height h1 of the evaporator 5. In this embodiment, the height h1 of the evaporator 5 is equal to the height h2 of the second condensing portion 3b. The height of the first condensation portion 3a is equal to the height h1 of the evaporator 5 and the height h2 of the second condensation portion 3b. In the height direction of the condenser 3, the third condensing portion 3c projects more upward than the evaporator 5.

The width w2 of the second condensation portion 3 b 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 portion 3a. The width of the third condensation portion 3c is equal to the width w2 of the second condensation portion 3b. In the width direction of the condenser 3, the second condensation part 3b and the third condensation part 3c protrude further to the right and left than the evaporator 5.

According to the dehumidifying device 1 according to this embodiment, the condenser 3 is located between the evaporator 5 and the blower 6 and is arranged to overlap the evaporator 5 in a direction from the evaporator 5 to the blower 6, which is more than the evaporator 5. Protrudes outward. Therefore, in the flow direction of the air from the evaporator 5 to the blower 6, the air can be caused to flow to the condenser 3 without being hindered by the evaporator 5. Therefore, the configuration of the air passage becomes easy.

In a case where at least one of the upper and lower portions of the condenser 3 is more prominent than the evaporator 5, at least one of the upper and lower portions of the condenser 3 may be taken into the second air path 11b of the indoor air. The second suction port 14 b is arranged on the back surface 20 a of the housing 20. When the condenser 3 is more prominent than the evaporator 5 in the width direction (left-right direction) of the condenser 3, that is, when the width of the condenser 3 is larger than the width of the evaporator 5, the At least one of the left and right sides of the second intake port 14b for taking in the air from the room into the second air path 11b is arranged on the back surface 20a of the housing 20. Therefore, the dehumidifier 1 of this embodiment can be configured without substantially changing the configuration of the conventional dehumidifier.

In addition, by arranging the second suction port 14b of the second air path 11b so as to be aligned with the refrigerant inlet of the condenser 3, the heat exchange efficiency can be improved. That is, when the flow of the refrigerant in the condenser 3 arranged in the most downstream of the second air path 11 b is in the up-down direction, the inlet of the high-temperature refrigerant is arranged above the condenser 3. Therefore, by arranging the second air path 11b so as to be aligned with the upper portion of the condenser 3, the heat exchange efficiency can be improved. Moreover, when the refrigerant | coolant of the condenser 3 arrange | positioned at the most downstream of the 2nd air path 11b flows from right to left, the inlet of a high temperature refrigerant is arrange | positioned on the right side of the condenser 3. Therefore, by arranging the second air path 11b to the right side of the condenser 3, the heat exchange efficiency can be improved.

Third Embodiment

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

Between the evaporator 5 and the first condensing section 3a, air at a temperature (for example, 13 ° C) lower than the room temperature (for example, 27 ° C) for heat exchange between the evaporator 5 and the refrigerant flows to the first condensing section 3a. Between the first condensation part 3a and the second condensation part 3b, air at a higher temperature (for example, 28 ° C) than the room temperature (for example, 27 ° C) for heat exchange between the first condensation part 3a and the refrigerant is condensed toward the second The portion 3b flows.

Between the evaporator 5 and the first condensing portion 3a, since the difference between the condensation temperature and the air temperature becomes smaller when the air passing through the evaporator 5 is mixed with the indoor air, the performance of the condenser decreases, and the evaporator 5 and the first The interval t1 of the coagulation portion 3a can also be made smaller. On the other hand, between the first condensation part 3a and the second condensation part 3b, by increasing the interval t2 between the first condensation part 3a and the second condensation part 3b, the air and the air after the first condensation part 3a is passed through are provided. Mixed area of outdoor air. Thereby, since the difference between the condensation temperature and the air temperature of the second condensation portion 3b becomes large, the condensation performance can be improved.

According to the dehumidifying device 1 according to this embodiment, the interval t2 between the first condensation portion 3a and the second condensation portion 3b is larger than the interval t1 between the first condensation portion 3a and the evaporator 5. Therefore, by preventing the air passing through the evaporator 5 from mixing with the indoor air between the first condensing portion 3a and the evaporator 5, the difference between the condensation temperature of the first condensing portion 3a and the air temperature can be reduced. This can suppress a decrease in the coagulation performance. The difference between the condensation temperature of the second condensation portion 3b and the air temperature is promoted between the first condensation portion 3a and the second condensation portion 3b by promoting the mixing of the air passing through the first condensation portion 3a and the indoor air. Get bigger. Thereby, coagulation performance can be improved. Moreover, since it can be provided in the assisted area of the air passing through the first condensation part 3a and the second condensation part 3b, the wind speed distribution of the air passing through the second condensation part 3b can be made uniform.

Fourth Embodiment

Referring to FIG. 14 and FIG. 15, in the dehumidifying device 1 of the fourth embodiment, the air inlets for the air to the second condensation part 3 b and the third condensation part 3 c, which are arranged at the most downstream of the air flow, are provided on the back surface. 20a and 20c.

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

In addition, in the dehumidifying device 1 of this embodiment, as in the third embodiment described above, the interval t2 between the first condensation section 3a and the second condensation section 3b is greater than the interval t1 between the first condensation section 3a and the evaporator 5. Bigger.

According to the dehumidifying device 1 according to this embodiment, not only the first suction port 14a and the second suction port 14b, but also the third suction means for sucking air into the first air path 11a and the second air path 11b are provided in the housing 20. The opening 15 can increase the air volume of the air passing through the second condensation part 3b and the third condensation part 3c. Thereby, coagulation performance can be improved.

In addition, the first suction port 14a, the second suction port 14b, and the third suction port 15 can be easily manufactured by providing the openings in the housing 20, so that the structure of the conventional dehumidifier can be changed without significantly changing the structure. The dehumidifier 1 of this embodiment is made into a product.

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 includes a third partition portion 16 for separating the air of the subcooling portion of the first condensation portion 3 a flowing through the refrigerant in a supercooled liquid state. The third partition portion 16 is arranged between the first condensation portion 3a and the second condensation portion 3b so as to block a space between the first condensation portion 3a and the second condensation portion 3b. The third suction port 15 is provided above the third partition 16.

According to the dehumidifier 1 according to the modification of the fourth embodiment, the third partition 16 prevents the subcooling section in the first condensation section 3a from performing heat exchange with the refrigerant at a temperature lower than room temperature, and indoors Mixing of air can improve the coagulation performance.

5th Embodiment

The dehumidifier 1 according to the fifth embodiment includes a structure shown in FIG. 2. In the dehumidifier 1 of the fifth embodiment, the refrigerant inlet x2 of the condenser 3 is arranged on the upper side of the condenser 3, and the refrigerant outlet y2 of the condenser 3 is arranged on the lower side of 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 condensation part 3c, and the refrigerant outlet y2 of the condenser 3 is provided in the first condensation part 3a. The refrigerant inlet z of the evaporator 5 is arranged below the evaporator 5.

According to the dehumidifying device of this embodiment, the refrigerant flows through the third condensation part 3c, the second condensation part 3b, and the first condensation part 3a in this order. Therefore, the refrigerant flowing through the third condensing portion 3c flows opposite to the air flowing through the second air path 11b. The refrigerant flowing through the second condensation part 3b and the first condensation part 3a flows opposite to the air flowing through the first air path 11a and the air flowing through the second air path 11b. Thereby, heat exchange with high temperature efficiency can be performed, and condensing efficiency can be improved.

The inlet of the refrigerant is provided in the third condensing section 3c arranged in the second air path 11b. Therefore, the refrigerant having a high temperature in the condenser 3 can perform heat exchange with the air of the room temperature flowing through the second air path 11b. . This improves heat exchange performance.

Moreover, since the refrigerant outlet y2 of the condenser 3 is arranged on the lower side of the condenser 3, it is easy to connect the refrigerant inlet y2 of the condenser 3 to the refrigerant inlet z arranged on the lower side of the evaporator 5. Moreover, since the refrigerant outlet y2 of the condenser 3 is provided in the first condensation part 3a, the pipe connecting the first condensation part 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 caused to face each other. Thereby, evaporation performance can be improved. In general, the refrigerant flowing in the evaporator 5 flows from the bottom to the top for the stability of the flow. According to the arrangement of the condenser 3 and the evaporator 5 according to this embodiment, the refrigerant can flow from the bottom to the top of the evaporator 5.

Sixth embodiment

Referring to Fig. 17, in the dehumidifier 1 of the sixth embodiment, the number of allocations of each of the second condensation part 3b and the third condensation part 3c is larger than that of the first condensation part 3a. In other words, the number of the heat transfer tubes flowing the refrigerant in each of the second condensing portion 3b and the third condensing portion 3c to the inside is larger than the number of heat transfer tubes flowing the refrigerant in the first condensing portion 3a to the inside.

In addition, as shown in FIG. 17, the number of allocations may be changed for each of the first condensation part 3 a, the second condensation part 3 b, and the third condensation part 3 c. In addition, referring to Fig. 18, the number of allocations may be reduced in the middle of the first condensation portion 3a.

According to the dehumidifying device 1 according to this embodiment, the number of allocations of each of the second coagulation portion 3b and the third coagulation portion 3c is larger than the number of allocations of the first coagulation portion 3a. Therefore, in a region where the refrigerant has a high flow rate and a large pressure loss because the refrigerant is in a superheated gas state or a gas-liquid two-phase state, reducing the flow rate of the refrigerant can reduce the pressure loss. On the other hand, in a region where the flow rate of the refrigerant is slow and the pressure loss is small because the refrigerant is in the supercooled liquid state, by increasing the flow rate of the refrigerant, efficient heat exchange can be performed.

Seventh embodiment

Referring to FIG. 19, in the dehumidifier 1 according to the seventh embodiment, the third condensation portion 3c is connected to the second air passage 11b, and is configured to extend the second partition portion 13 on the side opposite to the blower 6.

Since the first condensing portion 3a, the second condensing portion 3b, and the evaporator 5 are disposed in the second air path 11b, the pressure loss of the air flowing in the second air path 11b is greater than that of the air flowing in the first air path 11a. Less pressure loss. Therefore, because the amount of air flowing through the second air path 11b increases, the amount of air flowing through the first air path 11a decreases. Therefore, the amount of dehumidification is reduced because the volume of air flowing through the evaporator 5 disposed in the first air path 11a is reduced. For example, if the total number of rows of the evaporator 5, the first condensation part 3a, the second condensation part, and the number of fins is equal to the number of rows of the third condensation part 3c, and the number of fins, the same area Become the same ventilation resistance. Therefore, the air flowing through the first air path 11a and the second air path 11b can be easily adjusted according to the percentage of the area of the front surface of the evaporator 5, the first condensation part 3a, and the second condensation part 3b and the front surface area of the third condensation part. Amount of wind.

According to the dehumidifier 1 according to this embodiment, the third condensation portion 3c is connected to the second air path 11b, and is configured to extend the second partition portion 13 on the side opposite to the blower 6. Therefore, the pressure loss in the second air passage 11b can be increased. In the first air passage 11a, the pressure loss is increased because the first condensing portion 3a, the second condensing portion 3b, and the evaporator 5 are disposed. By increasing the pressure loss in the second air passage 11b, the air flow can be suppressed. Deflection of the second air path 11b. This can suppress a decrease in the amount of dehumidification in the evaporator 5. Therefore, a highly efficient dehumidifier 1 can be obtained.

Eighth embodiment

Referring to FIG. 20, in the dehumidifier 1 according to the eighth embodiment, the refrigerant circuit 10 is configured so that the refrigerant flowing from the evaporator 5 flows to the compressor 2 through the condenser 3. In the dehumidifier 1 of this embodiment, the condenser 3 includes a high-low pressure heat exchange unit 17. The high-low pressure heat exchange unit 17 includes a first flow path connected to the refrigerant outlet of the first condensing portion 3a and a refrigerant inlet of the pressure reducing device 4; and a second flow path connected to the refrigerant outlet of the evaporator 5 and the compressor 2 Suction inlet (refrigerant inlet).

In the high-low pressure heat exchange unit 17, heat is exchanged 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 performance (dehumidification amount) of the refrigerant by flowing in the evaporator 5 can be increased by the enthalpy difference.

In addition, the suction port (refrigerant inlet) of the compressor 2 is a refrigerant that is required to be vaporized in the evaporator 5 in order to maintain reliability. However, in the evaporator 5, the gas part of the refrigerant becomes locally high in temperature, which reduces the heat exchange performance.

In the refrigerant circuit 10 of this embodiment, even if the refrigerant flowing out of the evaporator 5 is in a gas-liquid two-phase state, the vaporized refrigerant can be returned to the refrigerant suction port of the compressor 2. Therefore, the performance of the evaporator 5 is not degraded, and the reliability of the compressor 2 is not impaired. In addition, even if the distribution of the refrigerant in the evaporator 5 is deteriorated, the refrigerant in the gas-liquid two-phase state is caused to flow to the evaporator 5, so that the performance of the evaporator 5 can be used to the maximum.

As described above, according to the dehumidifier 1 according to this embodiment, the refrigerant circuit 10 is configured to allow the refrigerant flowing out from the evaporator 5 to flow through the condenser 3 to the compressor 2. Therefore, the liquid refrigerant can be supplied to a region where the heat exchange efficiency is reduced by the occurrence of the superheated gas in the evaporator 5. Thereby, the heat exchange performance of the evaporator 5 can be improved.

It should be considered that the embodiments disclosed this time are examples on all matters and are not intended to be limiting. The scope of the present invention is not based on the above description, but is expressed according to the scope of the patent application. The intention is to include all changes within the meaning and scope of the scope of the patent application.

Claims (8)

A dehumidifying device includes: a frame body; a refrigerant circuit including a compressor, a condenser, a pressure reducing device, and an evaporator contained in the frame body; and a blower including a fan rotating around a shaft, And is contained in the interior of the frame; in the refrigerant circuit, the refrigerant flows through the compressor, the condenser, the pressure reducing device, and the evaporator in sequence; the condenser includes: a first condensation section, The refrigerant flow in the supercooled liquid state; the second condensation part, the refrigerant flow in the gas-liquid two-phase state; and the third condensation part, the refrigerant flow in the superheated gas state; the frame system includes: the first partition The unit includes a first air path, and the fan rotates around the shaft, and the air taken in from the outside of the frame body passes through the evaporator, the first condensing unit, and the first 2 condensation section; and a second air path, through which the fan rotates around the shaft, the air taken in from the outside of the housing through the third condensation section; the second partition section, the The connection is arranged to be separated by the first partition. Openings of the first area of the first air passage and the second area of the second air passage and the second area where the blower is arranged, and separating the first area from the second area; in a direction extending along the axis When the opening of the second partition is viewed from the first area, the fan is disposed in the opening; the direction of air flow in the first air path and the air flow in the second air path The directions are parallel; the air passing through the first air path and the air passing through the second air path are sent out in the same direction by the blower; the air passing through the first air path and the air passing through the second air path Air is blown out to the indoor space from the blow-out port of this housing. For example, the dehumidifying device of the first patent application range, wherein the condenser is located between the evaporator and the blower and is arranged to overlap the evaporator in a direction from the evaporator to the blower, which is greater than the evaporation. The device protrudes more outward. For example, in the dehumidifying device of the first scope of the application for a patent, the first condensation part is disposed between the evaporator and the second condensation part; the distance between the first condensation part and the second condensation part is greater than that of the first condensation part The distance between the condensation section and the evaporator is larger. For example, the dehumidification device of the first scope of the patent application, wherein the frame system includes a back surface on which the first suction port and the second suction port are provided, and a side surface on which the third suction port is provided; In order to suck air into the first air path, the second suction port is configured to suck air into the second air path; on the side, the third suction port is configured to suck air into the first air path and the first air path. 2 air passages; the third suction port is configured in the first air passage to suck air between the first condensation part and the second condensation part. For example, in the dehumidifier of the first scope of the patent application, in the condenser, the refrigerant flows through the third condensation part, the second condensation part, and the first condensation part in sequence; the inlet of the refrigerant is arranged in the condenser. An upper side of the condenser is provided on the third condensing portion; an outlet of the refrigerant is arranged on the lower side of the condenser and is provided on the first condensing portion. For example, in the dehumidifying device of the first scope of the patent application, the number of allocations of each of the second condensation part and the third condensation part is greater than that of the first condensation part. For example, in the dehumidifying device according to the first item of the patent application, the third condensation portion is connected to the second air path, and the second partition portion is configured to extend on the opposite side of the blower. For example, the dehumidification device according to the first patent application range, wherein the refrigerant circuit is configured to circulate the refrigerant flowing out from the evaporator to the compressor through the condenser.