JP6754948B2 - Dehumidifier - Google Patents

Description

The present invention relates to a dehumidifying device used for a living space or the like.

Dehumidifiers have been put into practical use to reduce the humidity of living spaces and increase comfort.

As an example of the conventional dehumidifying device, the main body case, the dehumidifying part provided in the main body case, and the air outside the main body case sucked from the air suction port are passed through the dehumidifying part and then outside the main body case from the air outlet. Some are equipped with a blower that blows out.

Further, the dehumidifying section is composed of a refrigerating cycle in which a compressor, a radiator, an expander and a heat absorber are sequentially connected in an annular shape. A part of the air sucked into the main body case from the air suction port by the blower is blown out of the main body case from the air outlet through the heat absorber, the first passage of the heat exchanger, and the radiator. Further, the other part of the air sucked from the air suction port by the blower is blown out from the main body case from the air outlet through the second passage of the heat exchanger and the radiator (for example, Patent Document 1 below). ..

In the above-mentioned conventional dehumidifier, a part of the air sucked into the main body case from the air suction port by the blower is cooled by a heat absorber to cause dew condensation, and then air is blown through the first passage of the heat exchanger and the radiator. Blow out of the main body case from the exit.

Further, in the conventional dehumidifier, the other part of the air sucked from the air suction port by the blower is passed through the second passage of the heat exchanger and blown out from the air outlet through the radiator to the outside of the main body case.

That is, the indoor air passing through the second passage of the heat exchanger is cooled by the air flowing from the heat absorber to the first passage of the heat exchanger, and dew condensation is also attempted here.

However, there is a problem that the indoor air passing through the second passage of the heat exchanger is blown out of the main body case from the air outlet in a state where dew condensation is not sufficiently formed.

That is, the air flowing into the first passage of the heat exchanger is the air after dew condensation is formed by the heat exchanger, but the temperature is not as low as that of the heat absorber even if it is cooled by the heat exchanger. Therefore, even if the air flowing into the first passage is cooled by the air flowing into the second passage, the air flowing into the second passage may not be condensed. In this case, the air passing through the second passage is discharged into the room without being dehumidified, and the dehumidifying effect is low.

A microfilm that copies the specification originally attached to the application at the time of filing of No. 56-20628.

Therefore, the present invention provides a dehumidifying device having an enhanced dehumidifying effect.

The dehumidifying device according to one aspect of the present invention dehumidifies the air in the main body case by a main body case having an air suction port and an air outlet, and a refrigeration cycle in which a compressor, a radiator, an expander, and a heat absorber are connected in order. It is equipped with a dehumidifying part. It is also equipped with a blower that blows the air outside the main body case sucked from the air suction port to the outside of the main body case from the air outlet after passing through the dehumidifying part. Further, a first passage and a second passage independent of the first passage are provided, and a heat exchanger for heat exchange between the air flowing through the first passage and the air flowing through the second passage is provided. It also has a first dehumidification path that blows a part of the air sucked into the main body case from the air suction port by the blower from the air outlet through the heat absorber, the first passage of the heat exchanger, and the radiator. There is. It also has a second dehumidification path that blows out other parts of the air sucked into the main body case from the air suction port by the blower from the air outlet through the second passage of the heat exchanger and the radiator. .. Further, the amount of air flowing through the second passage of the heat exchanger is smaller than the amount of air flowing through the first passage of the heat exchanger. Further, an air flow rate adjusting unit for increasing or decreasing the air flowing through the second passage is provided. Further, the air flow rate adjusting unit is composed of an opening / closing unit that opens / closes the second passage and a driving unit that drives the opening / closing unit. Further, when the temperature detected by the drive unit, the blower, the compressor, the first temperature sensor that detects the temperature of the air entering the air suction port, and the first temperature sensor becomes equal to or lower than the first set temperature, the drive unit is driven. It is equipped with a control unit that closes the opening / closing unit by the unit.

As described above, the air flowing through the first passage of the heat exchanger can sufficiently condense the air flowing through the second passage. That is, dew condensation can be caused even in the heat exchanger portion, and the dehumidifying effect can be enhanced as a whole.

FIG. 1 is a perspective view of a dehumidifying device according to the first embodiment of the present invention. FIG. 2 is a cross-sectional view taken along the line 2-2 of FIG. FIG. 3 is an exploded perspective view of the heat exchanger of the dehumidifying device according to the first embodiment of the present invention. FIG. 4 is a cross-sectional view of the dehumidifying device according to the second embodiment of the present invention. FIG. 5 is a control block diagram of the dehumidifying device according to the second embodiment of the present invention. FIG. 6 is a diagram illustrating an operating state of the dehumidifying device according to the second embodiment of the present invention. FIG. 7 is an operation flowchart of the dehumidifying device according to the second embodiment of the present invention. FIG. 8 is a cross-sectional view of the dehumidifying device according to the third embodiment of the present invention. FIG. 9 is a cross-sectional view of the dehumidifying device according to the fourth embodiment of the present invention.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. The following embodiments are examples that embody the present invention, and do not limit the technical scope of the present invention. Further, throughout the drawings, the same components are designated by the same reference numerals and the description thereof will be omitted. Further, in each drawing, the details of each part not directly related to the present invention are omitted.

(First Embodiment)
As shown in FIG. 1, the dehumidifying device 50 according to the present embodiment has a box-shaped main body case 1 as an outer shell, and the main body case 1 distinguishes between the outside of the main body case 1 and the inside of the main body case 1. On the back side of the main body case 1, an air suction port 2 is arranged at the upper part, and an air suction port 3 is arranged at the lower part of the air suction port 2. An air outlet 4 is arranged on the front side of the main body case 1 facing the back surface. An operation unit 25 is arranged on the upper part of the main body case 1.

The air suction port 2 and the air suction port 3 are provided as a rectangular flat surface that sucks air from a direction perpendicular to the back surface.

Above the air outlet 4, a louver 31 for changing the direction of the air blown from the air outlet 4 is provided.

The operation unit 25 receives input from the user, for example, and displays information on the dehumidifying device such as the operation mode and the current humidity to the user.

Further, as shown in FIG. 2, the main body case 1 of the dehumidifying device 50 includes an air passage 34, a blower 6, and a dehumidifying unit 5.

The air passage 34 communicates the air suction port 2 and the air suction port 3 with the air outlet 4. Further, in the present embodiment, the air passage 34 is composed of two dehumidifying paths, that is, a first dehumidifying path and a second dehumidifying path, which will be described in detail later.

The blower 6 includes a motor 32 and a fan 33 connected to a rotating shaft of the motor 32 to suck and exhaust air. The blower 6 blows the air outside the main body case 1 sucked from the air suction port 2 and the air suction port 3 to the outside of the main body case 1 from the air outlet 4 after passing through the dehumidifying unit 5. This air passage is the air passage 34.

The dehumidifying section 5 is composed of a refrigerating cycle in which a compressor 7, a radiator 8, an expander 9, and a heat absorber 10 are connected in this order in an annular shape. For example, an alternative chlorofluorocarbon (HFC134a) is used as a refrigerant in the refrigeration cycle.

In the main body case 1, a heat absorber 10 is provided on the air suction port 2 and the air suction port 3 side (upstream side in the air flow direction) of the air passage 34. A radiator 8 is provided on the air outlet 4 side (downstream side in the air flow direction) of the air passage 34.

A space is provided between the heat absorber 10 and the radiator 8, and the sensible heat type heat exchanger 11 is arranged in this space.

That is, in the main body case 1, a heat exchanger 10 is provided on the air suction port 2 and the air suction port 3 side of the air passage 34 communicating from the air suction port 2 and the air suction port 3 to the air outlet 4, and then , The heat exchanger 11 is provided, and then the radiator 8 is provided.

A funnel-shaped water collecting portion 12a is provided below the heat absorber 10 and the heat exchanger 11 in the main body case 1. Further, a water collecting tank 12b is detachably arranged below the water collecting portion 12a with respect to the main body case 1.

That is, the dehumidifying device 50 has a configuration in which dew condensation is generated by the heat absorber 10 and the heat exchanger 11, and the dew condensation water generated by the dew condensation is collected by the water collecting unit 12a and flows into the water collecting tank 12b.

Subsequently, the detailed structure of the heat exchanger 11 will be described with reference to FIG. As shown in FIG. 3, the heat exchanger 11 is configured by alternately polymerizing a plurality of synthetic resin plate 13s that form a vertical air passage and synthetic resin plates 14 that form a horizontal air passage. To.

Further, on the surface of the synthetic resin plate body 13 that forms the vertical air passage, a plurality of ribs 15 extending in the vertical direction are integrally formed with the plate body 13 at predetermined intervals. When one surface of the rib 15 is in close contact with the back surface of the adjacent plate body 14, the surface of the plate body 13 and the rib 15 and the back surface of the plate body 14 form a vertical air passage 13a, that is, a second passage.

Similarly, on the surface of the synthetic resin plate 14 that forms the lateral air passage, a plurality of ribs 16 extending in the lateral direction are formed integrally with the plate 14 at predetermined intervals. When one surface of the rib 16 is in close contact with the back surface of the adjacent plate body 13, the surface of the plate body 14 and the rib 16 and the back surface of the plate body 13 form a lateral air passage 14a, that is, a first passage.

The vertical air passage 13a and the horizontal air passage 14a have independent air passage spaces, that is, there is no air flow.

The heat exchanger 11 configured in this way has a rectangular parallelepiped shape. However, the rectangular parallelepiped shape referred to here does not have to be exactly rectangular on all surfaces, and it is not necessary that all adjacent surfaces intersect at right angles. In other words, the rectangular parallelepiped shape may be a hexahedron at first glance.

In the heat exchanger 11, an opening 17 for the first passage is formed on the opposite long sides of the rectangular parallelepiped shape. Further, in the heat exchanger 11, an opening 18 for the second passage is formed on the opposite short sides of the rectangular parallelepiped shape. That is, the second passage has a longer air passage than the first passage.

As for the opening 17, the heat absorber 10 side constitutes the upstream opening 17a, and the radiator 8 side constitutes the downstream opening 17b.

As for the opening 18, the air suction port 2 side constitutes the upstream opening 18a, and the water collecting portion 12a side (vertically downward direction) constitutes the downstream opening 18b.

Subsequently, the operation of the dehumidifying device will be described with reference to FIG.

By driving the blower 6, air X is sucked into the main body case 1 from the air suction port 3. The air X is sent from the air outlet 4 to the outside of the main body case 1 via the heat absorber 10, the upstream opening 17a of the heat exchanger 11, the first lateral passage, the downstream opening 17b, the radiator 8, and the blower 6. It is blown out. This air X path is the first dehumidification path described above. The air X can be defined as the air sucked from the air suction port 3 among the air suction port 2 and the air suction port 3, that is, a part of the sucked air.

Then, the air X flowing through such a path is first cooled by the heat absorber 10 to cause dew condensation. As shown in FIG. 2, the condensed water generated by the occurrence of dew condensation is dropped downward, collected by the funnel-shaped water collecting portion 12a, and flowed into the water collecting tank 12b.

Further, since the dry air X after the dew condensation is generated is blown out from the air outlet 4 to the outside of the main body case 1, for example, the humidity in the room can be lowered.

On the other hand, by driving the blower 6, air Y is sucked into the main body case 1 from the air suction port 2. The air Y passes through the second vertical passage from the upstream opening 18a of the heat exchanger 11 and passes through the downstream opening 18b, the radiator 8, and the blower 6 from the air outlet 4 to the outside of the main body case 1. It is blown out. This air Y path is the above-mentioned second dehumidification path. The air Y can be defined as the air sucked from the air suction port 2 among the air suction port 2 and the air suction port 3, that is, the other part of the sucked air. In the present embodiment, the total amount of air sucked into the dehumidifying device 50 is obtained by adding two pieces of air, a part of air and another part of air.

Then, as described with reference to FIG. 3, the first horizontal passage (passage of air X) of the heat exchanger 11 and the second vertical passage (passage of air Y) intersect. Therefore, heat exchange is possible between the air (air X) flowing through the first passage and the air (air Y) flowing through the second passage.

Here, the air X flowing through the first lateral passage of the heat exchanger 11 is cooled by passing through the heat absorber 10 as described above. Therefore, the heat exchanger 11 can lower the temperature of the air Y flowing through the second passage that has not passed through the heat absorber 10 by heat exchange. By positively utilizing this point, the heat exchanger 11 also causes dew condensation on the air Y flowing through the second passage.

In order to generate dew condensation, in the present embodiment, the amount of air Y flowing through the second passage of the heat exchanger 11 is smaller than the amount of air X flowing through the first passage of the heat exchanger 11.

Specifically, the heat exchanger 11 has made the ventilation resistance of the second passage (passage of air Y) larger than the ventilation resistance of the first passage (passage of air X).

That is, in the present embodiment, as shown in FIG. 2 above, the heat exchanger 11 has a rectangular parallelepiped shape. Then, as shown in FIG. 3, an opening 17 for the first passage was formed on the opposite long side, and an opening 18 for the second passage was formed on the opposite short side. By making the opening area of the opening 17 on the long side larger than the opening area of the opening 18 on the short side, the air resistance of the second passage is changed to the air resistance of the first passage from the viewpoint of the air flow to the blower 6. Making it bigger.

Then, since the ventilation resistance of the second passage (passage of air Y) of the heat exchanger 11 is made larger than the ventilation resistance of the first passage (passage of air X) in this way, the air Y flowing through the second passage is increased. Is less than the air X flowing through the first passage.

Therefore, the cooled air X flowing through the first passage can sufficiently cool the air Y less than the air X flowing through the second passage, and dew condensation can be generated.

As a result, as shown in FIG. 2, dew condensation water is also generated from the air Y flowing through the second passage. Then, the condensed water drops downward from the second passage, is collected by the funnel-shaped water collecting portion 12a, and flows into the water collecting tank 12b.

Further, the dry air Y after the dew condensation water is generated is blown out of the main body case 1 from the air outlet 4 through the downstream opening 18b of the heat exchanger 11, the radiator 8, and the blower 6. Thereby, for example, the humidity in the room can be lowered.

As shown in FIG. 2, the downstream opening 18b of the heat exchanger 11 has an inclined surface inclined toward the radiator 8 side.

That is, by inclining the downstream opening 18b toward the next radiator 8 side, the air Y flows smoothly toward the radiator 8 side.

Further, the inclined surface guides the condensed water generated and dropped in the second passage to the pointed tip portion 54 further downward at the downstream opening 18b. The dew condensation water guided to the tip portion 54 is combined with other dew condensation water to increase the weight. As a result, it is possible to promote the dripping of the condensed water to improve the drainage and prevent the water droplets from staying and causing air resistance.

In the present embodiment, the flow rate ratio of air X to air Y is set to 26:18 by the above configuration.

That is, the amount of air flowing through the second passage (passage of air Y) of the heat exchanger 11 is smaller than the amount of air flowing through the first passage (passage of air X) of the heat exchanger 11. As a result, even if the temperature of the air flowing through the first passage (passage of air X) of the heat exchanger 11 is slightly higher than that of the heat absorber 10, the air flowing through the second passage (passage of air B) is sufficiently dewed. Can be made to. As a result, dew condensation can be caused even in the 11th portion of the heat exchanger, and the dehumidifying effect can be enhanced as a whole.

Further, by providing the opening 17 for the first passage on the opposite long side, the passage length of the second passage is made longer than the passage length of the first passage. As a result, the cooling time in which the air Y flowing through the second passage is cooled by the air X becomes longer, and the dehumidification efficiency can be improved.

(Second embodiment)
Subsequently, the dehumidifying device according to the second embodiment will be described with reference to FIGS. 4, 5, 6, and 7.

The feature of the dehumidifying device 51 according to the present embodiment is that the dehumidifying device 50 according to the first embodiment is provided with an air flow rate adjusting unit for increasing or decreasing the amount of air flowing through the second passage of the heat exchanger 11. ..

Specifically, as shown in FIG. 4, the air flow rate adjusting unit is composed of an opening / closing unit 19 that opens / closes the second passage of the heat exchanger 11 and a driving unit 20 that drives the opening / closing unit 19.

The opening / closing portion 19 is a flat plate having an area including the upstream opening 18a, which is arranged between the air suction port 2 and the upstream opening 18a in the second passage. The opening / closing portion 19 is rotatably supported by a drive portion 20 provided on the end side of the upstream opening 18a opposite to the air suction port 2 as a rotation axis. By this rotation, the opening / closing portion 19 opens / closes the upstream opening 18a of the heat exchanger 11, that is, the second passage.

The opening / closing portion 19 is located so as to cover the upstream opening 18a in the closed state, that is, restricts the inflow of air into the heat exchanger 11. Further, the opening / closing portion 19 enables air to flow into the upstream opening 18a by lifting the short side close to the air suction port 2 upward with the driving portion 20 as the rotation axis in the open state.

The drive unit 20 functions as a rotation shaft of the opening / closing unit 19 and rotatably supports the opening / closing unit 19 in the vicinity of the upper end portion of the radiator 8. The drive unit 20 corresponds to, for example, a motor and a gear that is rotationally driven by the motor.

Further, as shown in FIG. 5, the drive unit 20 is connected to the control unit 21 together with the blower 6 and the compressor 7.

Further, the control unit 21 includes a first temperature sensor 22 that detects the temperature of the air entering the air suction port 3 portion shown in FIG. 4, and a second temperature sensor 23 that detects the temperature of the heat absorber 10 portion. The memory 24 and the operation unit 25 are connected.

The operation unit 25 is provided on the upper outer surface of the main body case 1, and provides information about the dehumidifying device to the user, for example, a physical switch for instructing the dehumidifying device 51 to change the operation mode or selecting a function. It has a display panel to display.

The control unit 21 is, for example, a microcomputer that controls the operation of the dehumidifying device 51 by reading and executing the operation program from the memory 24 in which the operation program is stored. The control unit 21 receives temperature signals from, for example, the first temperature sensor 22 and the second temperature sensor 23, and turns on / off the operations of the blower 6, the compressor 7, the drive unit 20, and the like based on the temperature signals. .. Details of each process performed by the control unit 21 will be described below.

Subsequently, the processing of the control unit 21 based on the temperature signals from each temperature sensor will be described.

When the temperature (t1) of the air entering the air suction port 3 portion detected by the first temperature sensor 22 is higher than the first set temperature (te, for example, 18 ° C.) when the dehumidifying device 51 is activated, the control unit 21 Performs the operation shown at "normal temperature" in FIG.

That is, the blower 6 and the compressor 7 are in the ON state, that is, they are driven, and the opening / closing unit 19 is opened as shown in FIG. By the opening operation, the opening / closing portion 19 opens the upstream opening 18a, and the above-mentioned dehumidifying operation is performed (steps S1 and S2 in FIG. 7).

Further, when the temperature (t1) of the air entering the air suction port 3 portion detected by the first temperature sensor 22 is equal to or lower than the first set temperature (te, for example, 18 ° C.), the control unit 21 may perform the operation of FIG. Perform the operation indicated by "low temperature".

That is, the blower 6 and the compressor 7 are driven, and the opening / closing unit 19 is closed by the driving unit 20. The opening / closing unit 19 closes the upstream opening 18a by the closing operation, and the dehumidifying operation is executed in this state (steps S2 and S3 in FIG. 7).

In this state, the air X sucked from the air suction port 3 by the blower 6 is first cooled by the heat absorber 10, so that dew condensation occurs here. The dew condensation water generated by the occurrence of dew condensation drops downward, is collected by the funnel-shaped water collecting portion 12a, and flows into the water collecting tank 12b.

Further, the dry air X after the dew condensation occurs is passed through the upstream opening 17a of the heat exchanger 11, the first lateral passage, the downstream opening 17b, the radiator 8, and the blower 6 to the air outlet 4. Blow out from the main body case 1. Thereby, for example, the humidity in the room can be lowered.

By the way, below the set temperature, that is, in a low temperature state, the frost formation phenomenon in which frost is attached easily occurs in the heat absorber 10. In this case, since the ventilation resistance of the heat absorber 10 increases, the balance of air resistance in the first passage and the second passage changes. That is, the air volume of the air X decreases and the air volume of the air Y increases. Then, as the air volume in the heat absorber 10 decreases, frost formation is further promoted. Therefore, in this low temperature situation, the opening / closing unit 19 is closed. That is, by closing the second dehumidification path, even if the blower 6 is driven, the air Y does not flow into the second passage of the heat exchanger 11. By doing so, all the suction force of the blower 6 can be used for the suction of the first path, and the amount of air passing through the heat absorber 10 can be increased. As a result, even when frost formation starts, the air flowing through the heat absorber 10 is increased, that is, the promotion of frost formation is suppressed, and the dehumidifying operation for eliminating frost formation is continued.

In this state, when the initial operation time (TS) elapses, for example, 25 minutes (step S4 in FIG. 7), the second temperature sensor 23 (ts) that detects the temperature of the heat absorber 10 portion is set to the second set temperature (step S4 in FIG. 7). It is determined whether or not t0 (for example, 0.5 ° C.) or less. The initial operation time (TS) is the time from the start of the operation indicated by the above-mentioned "low temperature".

When the temperature detected by the second temperature sensor 23 (ts) is equal to or lower than the second set temperature (t0, for example, 0.5 ° C.), the control unit 21 performs the operation represented by “de-ice” in FIG. (Step S5, step S6 in FIG. 7).

In this state, since the operation in the low temperature state is continued, the frost formation spreads on the surface of the heat absorber 10, so that the control unit 21 executes the deice operation for eliminating the frost formation.

In the de-ice operation, the control unit 21 drives the blower 6 in a state where the compressor 7 is stopped and the opening / closing unit 19 is closed (step S6 in FIG. 7).

During the de-ice operation, the air X sucked only from the air suction port 3 by the blower 6 is concentrated and blown to the heat absorber 10 to eliminate the frost formation on the surface of the heat absorber 10. The operating time of the deice operation is, for example, 10 minutes (Td: deice integration time).

Then, after the lapse of the de-ice integration time (Td), the control unit 21 acquires the temperature of the second temperature sensor 23 (ts) that detects the temperature of the heat absorber 10 portion. The control unit 21 determines whether the temperature detected by the second temperature sensor 23 (ts) is equal to or higher than the second set temperature (t0, for example, 0.5 ° C.) (steps S8 and S9 in FIG. 7), or the set time. When Td (for example, 10 minutes) elapses, the deice operation ends (steps S7 and S9 in FIG. 7).

As described above, the dehumidification operation can be performed while suppressing the promotion of frost formation and further eliminating the frost formation only by adjusting the amount of air with the air flow rate adjusting unit shown in the "low temperature" operation. That is, even when frost formation occurs, frost formation can be eliminated while continuing the dehumidifying operation, and dehumidification can be performed efficiently.

(Third embodiment)
Subsequently, the dehumidifying device according to the third embodiment will be described with reference to FIG.

As shown in FIG. 8, the feature of the dehumidifying device 52 according to the present embodiment is that in addition to the first dehumidifying path through which air X flows and the second dehumidifying path through which air Y flows in the configuration shown in the first embodiment, This is a point provided with a third dehumidifying path through which air Z flows. The air Z is another part of the air sucked from the air suction port 2 or 3. Then, in the present embodiment, the total amount of air sucked into the dehumidifying device 52 is obtained by adding three types of air: a part of air, another part of air, and another part of air. In other words, the other part of the air can be a part of the total amount of air sucked into the dehumidifying device 52, excluding a part of the air and another part of the air.

The other portion (air Z) of the air sucked from the air suction port 2 or the air suction port 3 by the blower 6 is air through the upper portion 8a of the radiator 8 without passing through the heat absorber 10 and the heat exchanger 11. Blow out from the air outlet 4 to the outside of the main body case 1.

The path through which the air Z passes, that is, the path through which the air blows out from the air outlet 4 to the outside of the main body case 1 through only the radiator 8 without passing through the heat absorber 10 and the heat exchanger 11, is the third dehumidification path.

Here, the radiator 8 projects vertically upward from the upper end of the heat absorber 10 and the upper end of the heat exchanger 11. This protruding portion corresponds to the upper portion 8a and can be a part of the radiator 8 above the center in the height direction of the radiator 8. In addition, the vertical upper direction means the upper part when the dehumidifying device 52 is installed in a state where it can be normally operated.

In this embodiment, the air Z passes through the upper portion 8a of the radiator 8. Air X and air Y will pass through other parts of the radiator 8 below the upper portion 8a of the radiator 8 through which the air Z passes.

Then, the air Z flowing in such a path cools the upper portion 8a of the radiator 8. Therefore, the radiator 8 is cooled, and as a result, the heat absorber 10 is cooled, and the dehumidifying capacity of the dehumidifying device 52 can be improved.

Specifically, the refrigerant that has become hot in the compressor 7 first flows into the upper portion 8a of the radiator 8. That is, in the radiator 8, the upper portion 8a has a higher temperature than the other parts of the radiator 8. Since the air Z cools the upper portion 8a of the radiator 8 having a relatively high temperature, the radiator 8 can be effectively cooled. As a result, the radiator 8 is cooled and the heat absorber 10 is cooled, so that the dehumidifying capacity of the dehumidifying device 52 can be improved.

Since the refrigerant heated to a high temperature by the compressor 7 is gasified, the compressor 7 is usually connected to the upper portion 8a of the radiator 8. Then, the refrigerant is liquefied by cooling in the radiator 8 and moves vertically downward. Therefore, in the present embodiment, the air Z passes through the upper portion 8a to enhance the cooling effect of the radiator 8. However, structurally, the upper portion 8a is not always connected to the compressor 7. In such a case, it is preferable to pass the air Z in the vicinity of the connection portion on the compressor 7 side of the connection portion on the compressor 7 side and the connection portion on the expander 9 side provided in the radiator 8. Since the temperature of the connection part on the compressor 7 side is higher than that of the connection part on the expander 9 side, the third dehumidification path passes through the connection part on the compressor 7 side of the radiator 8 to allow air to pass through. Z can effectively cool the radiator 8.

Further, by adding the air Z, the total amount of air (the amount of air X + air Y + air Z) can be increased.

Further, since the air Z cools the upper portion 8a of the radiator 8, the temperature rises when the air Z blows out from the air outlet 4 to the outside of the main body case 1 as compared with the case where the air Z is sucked from the air suction port 2 or 3.

As a result, as compared with the configuration of the first embodiment, air having a higher temperature, a lower humidity, and a larger total air volume is blown out of the main body case 1 from the air outlet 4. ..

Therefore, when the clothes are dried in a living space or the like by using the dehumidifying device, the effect of drying can be enhanced.

The amount of air Y flowing through the second passage of the heat exchanger 11 is smaller than the amount of air X flowing through the first passage of the heat exchanger 11.

In the present embodiment, the amount of air Z is further preferably smaller than the amount of air Y flowing through the second passage of the heat exchanger 11. Specifically, it is preferable to make the ventilation resistance of air Z larger than the ventilation resistance of air Y.

According to this configuration, the amount of air X and air Y that contribute to dehumidification can be sufficiently secured, so that the dehumidifying capacity of the dehumidifying device can be further effectively improved.

(Fourth Embodiment)
Subsequently, the dehumidifying device according to the fourth embodiment will be described with reference to FIG.

As shown in FIG. 9, the feature of the dehumidifying device 53 according to the present embodiment is that in the heat exchanger 11 in the configuration shown in the first embodiment, the upstream opening 18a of the second passage is the air suction port 2 It is a point where the inclined surface 55 is inclined toward the side.

Further, in the present embodiment, a circuit board 61 as a control unit for controlling the operation of the dehumidifying device 53 is provided above the heat exchanger 11 in the main body case 1. The circuit board 61 is arranged close to the heat exchanger 11.

The air Y sucked into the main body case 1 from the air suction port 2 by the blower 6 passes through the gap formed between the circuit board 61 and the heat exchanger 11, and heat exchanges through the upstream opening 18a of the second passage. It flows into the vessel 11. Then, the air is blown out of the main body case 1 from the air outlet 4 via the radiator 8 and the blower 6. On the other hand, the air X sucked into the main body case 1 from the air suction port 3 by the blower 6 passes through the heat absorber 10 and flows into the heat exchanger 11 from the upstream opening 17a of the first passage. After that, the air X flows out from the downstream opening 17b, and is blown out of the main body case 1 from the air outlet 4 via the radiator 8 and the blower 6. At this time, heat exchange is performed between the air X and the air Y in the heat exchanger 11, and dew condensation occurs in the second passage.

Here, of the air Y passing through the second passage, the air passing through the portion close to the radiator 8 is less likely to cause dew condensation because the cooling effect of the heat exchanger 11 is small.

That is, the air for cooling the air passing through the second passage is the air passing through the first passage. Then, the air X flowing through the first passage flows into the heat exchanger 11 from the upstream side opening 17a on the heat absorber 10 side, and flows out from the downstream side opening 17b on the radiator 8 side. Therefore, first, the air passing through the portion close to the heat absorber 10 in the second passage is cooled, and then the air passing through the portion close to the radiator 8 in the second passage is cooled.

Therefore, the air X flowing through the first passage is first heated by exchanging heat with the air passing through the portion close to the heat absorber 10 in the second passage, and in the warmed state, the portion close to the radiator 8 in the second passage. Will cool the air passing through. As a result, the temperature difference with the air passing through the portion of the second passage near the radiator 8 becomes small, and the heat exchange rate becomes slow. Since the heat exchange rate is slow, it is difficult to cool and dew condensation is unlikely to occur in the second passage.

Further, since the direction of the flow of the air Y taken in from the air suction port 2 suddenly changes when it flows into the second passage of the heat exchanger 11, the air volume is biased in the second passage.

That is, the air Y taken in from the air suction port 2 provided on the back surface of the main body case 1 flows in the lateral direction, but the upstream opening 18a of the second passage opens in the vertical direction (vertically upward). Therefore, the air flow is sharply bent. At this time, the flow of air Y is biased due to inertia, and more air flows into the portion of the second passage that is outside the bend and is close to the radiator 8. Since a large amount of air flows in the portion of the second passage near the radiator 8, a larger amount of cooling heat is required to cool the air to the dew point temperature to cause dew condensation. However, as described above, the air passing through the portion of the second passage near the radiator 8 is not easily cooled, so that dew condensation is unlikely to occur.

On the other hand, in the present embodiment, since the upstream opening 18a of the heat exchanger 11 is an inclined surface 55 inclined toward the air suction port 2, the air passing through the portion close to the radiator 8 in the second passage is passed. It becomes easier to cool. The details will be described below.

The length of the downstream opening 17b of the first passage in the long side direction is extended in the direction of the upper portion 8a of the radiator 8. The height after the extension may be higher than the downstream end of the heat absorber 10 (the upper end of the heat absorber 10 in FIG. 9). As a result, the upstream opening 18a is inclined toward the air suction port 2 side. Then, the passage length of the portion of the second passage near the radiator becomes longer, and the time for passing through the heat exchanger 11 can be lengthened. As a result, even if the temperature difference is small and the heat exchange rate is slow, heat exchange can be performed for a longer period of time, and as a result, the amount of heat exchange can be increased. Since the amount of heat exchange can be increased, the amount of cooling for the air flowing through the portion of the second passage near the radiator 8 can be increased, and the formation of dew condensation can be increased.

Further, since the length of the downstream opening 17b of the first passage in the long side direction is extended and the upstream opening 18a is inclined toward the air suction port 2, the portion close to the heat absorber 10 of the second passage It becomes easier for the air to flow in, and the bias of the air volume is eased. That is, in the second passage, from the heat absorber 10 toward the radiator 8, the passage length of the second passage becomes larger and the ventilation pressure loss becomes larger, so that the air Y is less likely to flow into the portion close to the radiator 8. .. On the contrary, since it is easy to flow into the portion close to the heat absorber 10, the bias of the air volume flowing through the second passage is alleviated. By alleviating the bias of the air volume, the amount of air flowing through the portion of the second passage near the radiator 8 is reduced, and the amount of cooling heat required for cooling to the dew point temperature is reduced. Therefore, it is possible to increase the formation of dew condensation due to the air flowing through the portion of the second passage near the radiator 8.

As described above, the formation of dew condensation due to the air flowing in the portion of the heat exchanger 11 near the radiator 8 in the second passage can be further increased, and the dehumidifying performance can be further improved.

(Modification example)
In addition, in the above-mentioned four embodiments, an example in which the air suction port is divided into two is shown. However, in the present embodiment, the distribution of the amount of air passing through each passage utilizes the air resistance of each passage. By doing so, it is not always necessary to divide the air suction port into two, and the same effect can be obtained as one air suction port.

Further, when the amount of air passing through each passage is distributed by using the opening area of the air suction port instead of the air resistance, a plurality of air suction ports may be provided according to each air amount.

Further, although the control unit is not described in the first embodiment and the third embodiment, the control unit shown in the second embodiment is prepared for the first embodiment and the third embodiment. Is also good. In this case, the control unit operates the dehumidifying device by transmitting a control command to the compressor or the blower. Of course, the control unit shown in the second embodiment may be incorporated into the control unit shown in the fourth embodiment.

Moreover, the above-mentioned four embodiments may be carried out at the same time within a consistent range. For example, providing a dehumidifying device provided with an air flow rate adjusting unit and a third dehumidifying path corresponds to this.

Since the present invention can cause dew condensation even in the heat exchanger portion, it is extremely useful as a dehumidifying device having a high dehumidifying effect.

1 Main body case 2, 3 Air suction port 4 Air outlet 5 Dehumidifier 6 Blower 7 Compressor 8 Heater 8a Upper 9 Expander 10 Heat exchanger 11 Heat exchanger 12a Water collector 12b Water collection tank 13, 14 Plate 13a Vertical air passage (second passage)
14a Sideways air passage (1st passage)
15, 16 Ribs 17, 18 Openings 17a, 18a Upstream openings 17b, 18b Downstream openings 19 Opening and closing 20 Drives 21 Controls 22 First temperature sensor 23 Second temperature sensor 24 Memory 25 Operation 31 Louver 32 Motor 33 Fan 34 Air passage 50, 51, 52, 53 Dehumidifier

Claims (6)

A body case with an air inlet and an air outlet,
A dehumidifying section that dehumidifies the air inside the main body case by a refrigeration cycle in which a compressor, a radiator, an expander, and a heat absorber are connected in order.
A blower that blows the air outside the main body case sucked from the air suction port to the outside of the main body case from the air outlet after passing through the dehumidifying portion.
A heat exchanger having a first passage and a second passage independent of the first passage and exchanging heat between the air flowing through the first passage and the air flowing through the second passage.
A part of the air sucked into the main body case from the air suction port by the blower is blown out of the main body case from the air outlet through the heat absorber, the first passage of the heat exchanger, and the radiator. The first dehumidification route and
A second portion of air sucked into the main body case from the air suction port by the blower is blown out of the main body case from the air outlet through the second passage of the heat exchanger and the radiator. With a dehumidifying route,
Amount of air flowing through the second passage of said heat exchanger, and configured to be less than the amount of air flowing through the first passage of said heat exchanger,
An air flow rate adjusting unit for increasing or decreasing the air flowing through the second passage is provided.
The air flow rate adjusting unit
It is composed of an opening / closing part that opens / closes the second passage and a driving part that drives the opening / closing part.
The drive unit, the blower, the compressor, and a first temperature sensor that detects the temperature of the air entering the air suction port.
A dehumidifying device including a control unit that closes the opening / closing unit by the driving unit when the temperature detected by the first temperature sensor becomes equal to or lower than the first set temperature . The opening / closing part
The dehumidifying device according to claim 1 , which is arranged between the air suction port and the second passage. A second temperature sensor for detecting the temperature of the heat absorber is provided.
The control unit
If the temperature detected by said first temperature sensor is equal to or less than the first predetermined temperature, in a closed state of the second copies passage of the heat exchanger by the switching unit, to drive the compressor and the blower,
If the temperature detected by the second temperature sensor falls below the second set temperature, with closed second copies passage of the heat exchanger by the switching unit, to drive the blower stops the compressor The dehumidifying device according to claim 1 , which is configured. Another portion of the air sucked into the main body case from the air suction port by the blower is passed from the air outlet to the main body case through the radiator without going through the heat absorber and the heat exchanger. The dehumidifying device according to claim 1, further comprising a third dehumidifying path for blowing out. The dehumidifying device according to claim 4 , wherein the third dehumidifying path is configured to pass through a connection portion on the compressor side of the radiator. The dehumidifying device according to claim 4 , wherein the amount of air flowing through the third dehumidifying passage is smaller than the amount of air flowing through the second passage.

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