TWI674382B - Dehumidifier - Google Patents

Abstract

The dehumidifying device of the present invention has a structure in which the amount of air flowing through the second passage of the heat exchanger is less than the amount of air flowing through the first passage. 2 passages, and heat exchange is performed between the air flowing through the first passage and the air flowing through the second passage. Therefore, even if the temperature of the air flowing through the first passage of the heat exchanger rises, the air flowing through the second passage can be sufficiently condensed. As a result, the heat exchanger can also be condensed, and the overall dehumidification effect can be improved.

Description

Dehumidifier Field of invention

The present invention relates to a dehumidifier for a living space and the like.

Background of the invention

The dehumidifier is practically used as a device that reduces the humidity of a living space and increases comfort.

An example of a conventional dehumidifier is shown in the microfilm of the original specification attached to the application at the time of application No. 56-20628 in Japan. It is provided with: a main body case; a dehumidification part provided in the main body case; And a blower, so that the air outside the main body casing sucked in from the air inlet passes through the dehumidifying part, and then blows out from the air outlet to the main body casing. The dehumidifier is constituted by a refrigeration cycle in which a compressor, a radiator, an expander, and a heat absorber are connected in a loop. Then, a part of the air sucked into the main body casing from the air suction port by a blower and blown out from the air outlet through the heat absorber, the first passage of the heat exchanger, and the radiator is adopted. The other part of the air sucked in from the air inlet by the blower is blown out from the air outlet to the main body through the second passage of the heat exchanger and the radiator. Constructed outside the case.

In the conventional dehumidifier, a part of the air sucked into the main body casing from the air suction port by a blower is cooled by a heat sink and condensed, and then blown from the air through the first passage of a heat exchanger and a radiator The outlet blows out of the main body casing.

In the conventional dehumidification device, the other part of the air sucked in from the air inlet through the blower is blown out of the main body casing through the second passage of the heat exchanger and from the air outlet through the radiator.

In short, the air flowing through the second passage of the heat exchanger is cooled by the air flowing from the heat sink to the first passage of the heat exchanger, and is condensed here.

However, the indoor air passing through the second passage of the heat exchanger is blown out from the air outlet to the outside of the main body in an insufficiently condensed state.

In other words, although the air flowing into the first passage of the heat exchanger is the air condensed by the heat sink, even if it is cooled by the heat sink, it still does not reach the low temperature of the heat sink. Therefore, even if the air flowing into the second passage is cooled with the air flowing into the first passage, the air flowing into the second passage may not condense. In this case, the air passing through the second passage is released into the room without being dehumidified, and the dehumidifying effect becomes low.

Summary of invention

Therefore, the present invention provides a dehumidifying device that improves the dehumidifying effect.

A dehumidification device according to one aspect of the present invention includes: a main body casing having an air suction port and an air blowing port; and a dehumidification unit, which sequentially connects a compressor, a radiator, an expander, and a heat sink to a refrigeration cycle, Dehumidify the air in the main body case. In addition, a blower is provided to allow the air outside the main body casing sucked in from the air suction port to pass through the dehumidifying part, and then blow out from the air outlet to the main body casing. In addition, a heat exchanger is provided, which includes a first passage and a second passage independent of the first passage, and performs heat exchange between the air flowing through the first passage and the air flowing through the second passage. In addition, a first dehumidifying path is provided, and a part of the air sucked into the main body casing from the air suction port by the blower is blown out from the air outlet through the heat absorber, the first passage of the heat exchanger, and the radiator. Outside the main body case. In addition, a second dehumidification path is provided, and the other part of the air sucked into the main body casing from the air suction port by the blower is blown out from the air outlet to the main body through the second passage of the heat exchanger and the radiator. Outside the shell. Furthermore, a configuration is adopted in which 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.

With the above, the air flowing through the first passage of the heat exchanger can sufficiently condense the air flowing through the second passage. In short, condensation can also occur in the heat exchanger, which can improve the overall dehumidification effect.

1‧‧‧ main body case

2, 3‧‧‧ air intake

4‧‧‧air blowing outlet

5‧‧‧ Dehumidification

6‧‧‧Air Supply Department

7‧‧‧compressor

8‧‧‧ Radiator

8a‧‧‧upper

9‧‧‧ Expander

10‧‧‧ heat sink

11‧‧‧ heat exchanger

12a‧‧‧Catchment Department

12b‧‧‧Gutter

13, 14‧‧‧ plate

13a‧‧‧Vertical Wind Road

14a‧‧‧Horizontal Wind Road

15, 16‧‧‧ ribs

17, 18‧‧‧ opening

17a, 18a‧‧‧upstream opening

17b, 18b‧‧‧ downstream opening

19‧‧‧Switch Department

20‧‧‧Driver

21‧‧‧Control Department

22‧‧‧The first temperature sensor

23, ts‧‧‧ 2nd temperature sensor

24‧‧‧Memory

25‧‧‧Operation Department

31‧‧‧louver

32‧‧‧ Motor

33‧‧‧fan

34‧‧‧air passage

50, 51, 52, 53‧‧‧ dehumidifier

54‧‧‧ Tip

55‧‧‧inclined surface

61‧‧‧circuit board

Steps S1 ~ S9‧‧‧‧

t0‧‧‧The second set temperature

t1‧‧‧Temperature

Td‧‧‧Defrost accumulation time

te‧‧‧first set temperature

TS‧‧‧ Initial operating time

X, Y, Z‧‧‧ Air

FIG. 1 is a perspective view of a dehumidifier according to a first embodiment of the present invention.

FIG. 2 is a sectional view taken along the line 2-2 in FIG. 1.

FIG. 3 is an exploded perspective view of a heat exchanger of the dehumidifier according to the first embodiment of the present invention.

Fig. 4 is a sectional view of a dehumidifier according to a second embodiment of the present invention.

Fig. 5 is a control block diagram of a dehumidifier according to a second embodiment of the present invention.

Fig. 6 is a diagram illustrating an operation state of a dehumidifier according to a second embodiment of the present invention.

FIG. 7 is an operation flowchart of the dehumidifier according to the second embodiment of the present invention.

Fig. 8 is a sectional view of a dehumidifier according to a third embodiment of the present invention.

Fig. 9 is a sectional view of a dehumidifier according to a fourth embodiment of the present invention.

Detailed description of the invention

Hereinafter, embodiments of the present invention will be described with reference to the drawings. The following embodiment is an example embodying the present invention and does not limit the technical scope of the present invention. In all drawings, the same constituent elements are assigned the same reference numerals, and descriptions thereof are omitted. In addition, in the drawings, the details of the parts that are not directly related to the present invention are omitted.

(First Embodiment)

As shown in FIG. 1, the dehumidifying device 50 of this embodiment has a box-shaped main body casing 1 as an outline, and the main body casing 1 distinguishes between the main body casing 1 outside and the main body casing 1. An air suction port 2 is arranged on the upper side of the back side of the main body cabinet 1, and an air suction port 3 is arranged below the air suction port 2. An air blow-out port 4 is disposed in the main body cabinet 1 and faces the front side from the rear side. An operation portion 25 is disposed on the upper portion of the main body cabinet 1.

Air inlet 2 and air inlet 3 are It is installed in the vertical plane of the intake air.

A louver 31 is provided above the air blow-out port 4, and changes the direction of the air blown from the air blow-out port 4.

The operation unit 25 receives, for example, an input from a user, or displays information about a dehumidifying device such as an operation mode or current humidity to the user.

As shown in FIG. 2, an air passage 34, a blower 6, and a dehumidifier 5 are provided in the main body case 1 of the dehumidifier 50.

The air passage 34 communicates with the air suction port 2 and the air suction port 3, and the air blowing port 4. In this embodiment, the air passage 34 is composed of two dehumidifying paths, that is, a first dehumidifying path and a second dehumidifying path. Details will be described later.

The air blowing unit 6 includes a motor 32 and a fan 33 connected to a rotating shaft of the motor 32 to suck and exhaust air. The air blowing unit 6 allows the air outside the main body casing 1 sucked in from the air suction port 2 and the air suction port 3 to pass through the dehumidifying part 5 and then blow out from the air blowing port 4 into the main body casing 1. This air passage is an air passage 34.

The dehumidifying section 5 is configured by connecting the compressor 7, the radiator 8, the expander 9, and the heat absorber 10 in this order as a ring-shaped refrigeration cycle. Refrigeration cycles use, for example, alternative halothane (HFC134a) as a refrigerant.

Furthermore, in the main body casing 1, a heat absorber 10 is provided on the air suction port 2 and the air suction port 3 side (the upstream side in the air flow direction) of the air passage 34. Then, 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 heat radiator 8, and a display is arranged in the space. Heat type heat exchanger 11.

In short, a heat absorber 10 is provided on the main body casing 1 at 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 blowing port 4. A heat exchanger 11 is provided, followed by a heat radiator 8.

Then, a funnel-shaped water collecting portion 12 a is provided in the main body casing 1 below the heat absorber 10 and the heat exchanger 11. Further, below the water collecting portion 12a, a water collecting tank 12b is detachably disposed to the main body casing 1.

In short, the dehumidifier 50 employs a configuration in which the heat absorber 10 and the heat exchanger 11 cause condensation to occur, and the condensate generated by the condensation is collected by the water collecting unit 12 a and allowed to flow into the water collecting tank 12 b.

Next, a detailed structure of the heat exchanger 11 will be described using FIG. 3. As shown in FIG. 3, the heat exchanger 11 is configured by alternately stacking a plurality of sheets of a synthetic resin plate body 13 forming a vertical air passage and a synthetic resin plate body 14 forming a horizontal air passage.

In addition, a plurality of ribs 15 extending in the longitudinal direction are formed integrally with the plate body 13 on the surface of the synthetic resin plate body 13 forming the vertical air path at predetermined intervals. One surface of the rib portion 15 is closely adhered to the back surface of the adjacent plate body 14, thereby forming a longitudinal air path 13a, that is, a second passage, by the surface of the plate body 13, the rib portion 15, and the back surface of the plate body 14.

Similarly, on the surface of the synthetic resin plate body 14 forming the lateral air path, a plurality of ribs 16 extending in the horizontal direction are formed integrally with the plate body 14 at predetermined intervals. One surface of the rib portion 16 is closely adhered to the rear surface of the adjacent plate body 13, thereby forming the surface of the plate body 14, the rib portion 16, and the rear surface of the plate body 13. The lateral air path 14a is the first passage.

The vertical air path 13a and the horizontal air path 14a are mutually independent in the air path space, that is, there is no air flow.

The heat exchanger 11 thus configured has a rectangular parallelepiped shape. However, in the so-called rectangular parallelepiped shape, all faces need not be strictly rectangular, and all adjacent faces need not intersect at right angles. In short, the shape of the cuboid may be a hexahedron at first glance.

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

The heat absorber 10 side of the opening 17 constitutes an upstream opening 17a, and the heat radiator 8 side constitutes a downstream opening 17b.

The air suction port 2 side of the opening portion 18 constitutes an upstream side opening portion 18a, and the water collecting portion 12a side (vertical downward direction) constitutes a downstream side opening portion 18b.

Next, the operation of the dehumidifier will be described using FIG. 2.

When the blower 6 is driven, the air X is sucked into the main body cabinet 1 from the air suction port 3. The air X is blown out from the air outlet 4 to the main body casing 1 through the heat absorber 10, the upstream opening 17a of the heat exchanger 11, the lateral first passage, the downstream opening 17b, the radiator 8, and the blower 6. . The path of the air X is the aforementioned first dehumidifying path. In addition, the air X is the air sucked in from the air suction port 3 in the air suction port 2 and the air suction port 3, and can be defined as a part of the inhaled air in general.

Then, the air X flowing through the path is first cooled in the heat sink 10, Condensation occurred. The condensed water generated due to the condensation drips downward as shown in FIG. 2, and is collected by the funnel-shaped water collecting part 12 a and flows into the water collecting tank 12 b.

In addition, since the dried air X after the condensation is blown out from the air outlet 4 to the outside of the main body casing 1, it is possible to reduce the indoor humidity, for example.

In addition, by driving the blower 6, air Y is sucked into the main body cabinet 1 from the air suction port 2. The air Y is blown out from the air outlet 4 through the downstream opening 18b, the radiator 8, and the blower 6 through the upstream second opening 18a of the heat exchanger 11 through the downstream opening 18b, the radiator 8, and the blower 6. The path of the air Y is the aforementioned second dehumidifying path. In addition, the air Y is the air sucked from the air suction port 2 among the air suction port 2 and the air suction port 3, and can be defined as other parts which suck air in general. In addition, in this embodiment, adding one part of air to the other part of the air, the total amount of air taken in by the dehumidifying device 50 is added.

Then, as illustrated in FIG. 3, the first passage in the horizontal direction (the passage of the air X) and the second passage in the vertical direction (the passage of the air Y) are configured to intersect. Therefore, the air (air X) flowing through the first passage and the air (air Y) flowing through the second passage can perform heat exchange.

Here, the air X flowing through the first passage in the lateral direction of the heat exchanger 11 is cooled by passing through the heat absorber 10 as described above. Therefore, the heat exchanger 11 can reduce the temperature of the air Y flowing through the second passage without passing through the heat sink 10 through heat exchange. By actively utilizing this, the heat exchanger 11 also causes condensation to occur in the air Y flowing through the second passage.

In order to cause condensation, in this embodiment, the amount of air Y flowing through the second passage of the heat exchanger 11 is smaller than that of the first air flowing through the heat exchanger 11 Composition of the amount of air X in the passage.

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

In short, in this embodiment, as shown in FIG. 2 described above, the heat exchanger 11 has a rectangular parallelepiped shape. Then, as shown in FIG. 3, an opening 17 for the first passage is formed on the opposite long side, and an opening 18 for the second passage is formed on the opposite short side. By making the opening area of the long-side opening portion 17 larger than that of the short-side opening portion 18, focusing on the airflow to the blower 6, the air impedance of the second passage is greater than the air impedance of the first passage.

Then, since the ventilation resistance of the second passage (the passage of air Y) of the heat exchanger 11 is made larger than the ventilation resistance of the first passage (the passage of air X), the air Y flowing through the second passage is more likely to flow through. There is little air X in the first passage.

Therefore, the cooled air X flowing through the first passage can sufficiently cool the air Y flowing through the second passage and less than the air X, so that condensation occurs.

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

The dry air Y after the condensed water is generated is blown out of the main body casing 1 through the air outlet 4 through the downstream opening 18b, the radiator 8, and the blower 6 of the heat exchanger 11. Thereby, for example, the indoor humidity can be reduced.

In addition, as shown in FIG. 2, the downstream-side opening portion 18 b of the heat exchanger 11 is an inclined surface inclined toward the radiator 8 side.

In short, by making the downstream side opening 18b, To the radiator 8 side, the air Y will smoothly flow toward the radiator 8 side.

Further, the inclined surface induces the condensed water generated and dripped in the second passage to the tip portion 54 protruding further downward in the downstream-side opening portion 18b. The condensed water induced to the tip portion 54 meets with other condensed water, and the weight increases. This promotes the condensation of water droplets, improves drainage, and the water droplets do not stay and become air resistance.

Furthermore, in this embodiment, by adopting the configuration as described above, the flow rate ratio of air X to air Y is 26 to 18.

In short, a configuration is adopted in which the amount of air flowing through the second passage (the passage of air Y) of the heat exchanger 11 is smaller than the amount of air flowing through the first passage (the passage of air X) of the heat exchanger 11. Thereby, even if the temperature of the air flowing through the first passage (air X passage) of the heat exchanger 11 is slightly higher than the temperature of the heat sink 10, the air flowing through the second passage (air B passage) can be sufficiently condensed. . As a result, the heat exchanger 11 can also be condensed, which can improve the overall dehumidification effect.

Moreover, by providing the opening 17 for the first passage on the opposite long side, the passage of the first passage can be made longer than that of the second passage. Thereby, the cooling time for the air Y flowing through the second passage to be cooled by the air X becomes longer, and the dehumidifying effect can be improved.

(Second Embodiment)

Next, a dehumidifier according to a second embodiment will be described with reference to FIGS. 4, 5, 6, and 7.

The dehumidifier 51 of this embodiment is characterized in that an air flow adjustment unit is provided in the dehumidifier 50 of the first embodiment to increase or decrease the amount of air flowing through the second passage of the heat exchanger 11.

Specifically, as shown in FIG. 4, the air flow adjustment unit is composed of a switch unit 19 and a drive unit 20. The switch unit 19 switches the second passage of the heat exchanger 11, and the drive unit 20 drives the switch unit 19.

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

In the closed state, the switch portion 19 covers the upstream opening portion 18 a, that is, restricts the inflow of air into the heat exchanger 11. In addition, when the switch portion 19 is opened, the short side near the air suction port 2 is lifted upward with the drive portion 20 as a rotation axis, thereby allowing air to flow into the upstream opening portion 18a.

The driving section 20 functions as a rotation axis of the switch section 19 and rotatably supports the switch section 19 near the upper end portion of the radiator 8. The driving unit 20 corresponds to, for example, a motor and a gear that is rotationally driven by the motor.

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.

Also connected to the control unit 21 are a first temperature sensor 22 that detects the temperature of the air entering the portion of the air inlet 3 shown in FIG. 4 and a second temperature sensor 23 that detects the portion of the heat sink 10 Temperature; memory 24; and operation section 25.

The operation section 25 is provided outside the upper part of the main body casing 1 and is provided with The user uses the display panel to instruct the dehumidifying device 51, for example, to change the operation mode, or to select a function such as a physical switch, and to display information about the dehumidifying device to the user.

The control unit 21 is, for example, a microcomputer, and loads and executes an operation program from the memory 24 storing the operation program, thereby controlling the operation of the dehumidifier 51. The control unit 21 receives, for example, a temperature signal from the first temperature sensor 22 or the second temperature sensor 23, and performs operations of the blower 6 or the compressor 7, the drive unit 20, and the like on / off based on the temperature signal. Details of each process performed by the control section 21 are described below.

Next, processing by the control unit 21 based on the temperature signal from each temperature sensor will be described.

When the dehumidifying device 51 is started, when the temperature (t1) of the air entering the air inlet 3 detected by the first temperature sensor 22 is higher than the first set temperature (te, for example, 18 ° C), the control unit 21 performs the operation shown in FIG. 6 "normal temperature".

In short, the blower 6 and the compressor 7 are in an ON state, that is, they are driven, and the switch unit 19 is opened as shown in FIG. 4. By the opening operation, the switch section 19 opens the upstream-side opening section 18a and performs the above-mentioned dehumidification operation (step S1 and step S2 in FIG. 7).

When the temperature (t1) of the air entering the air intake port 3 detected by the first temperature sensor 22 is equal to or lower than the first set temperature (re, for example, 18 ° C.), the control unit 21 performs the “low temperature” in FIG. 6. ”Shown action.

In short, the blower 6 and the compressor 7 are driven, and the switch unit 19 is turned off by the drive unit 20. With the closing action, the switch section 19 closes the upstream opening 18a, and performs a dehumidification operation in this state (step S2 and step S3 in FIG. 7).

In this state, the air X sucked from the air suction port 3 by the blower 6 is first cooled in the heat absorber 10, where it is condensed. The condensed water generated due to the condensation drips downward as shown in FIG. 2, and is collected by the funnel-shaped water collecting part 12 a and flows into the water collecting tank 12 b.

In addition, the condensed dry air X is blown out from the air outlet 4 to the main body through the upstream opening 17a, the first lateral passage, the downstream opening 17b, the radiator 8 and the blower 6 of the heat exchanger 11 Outside the case 1. Thereby, for example, the indoor humidity can be reduced.

However, if the temperature is below the set temperature, that is, in a low temperature state, the frosting phenomenon where the frost adheres easily occurs in the heat sink 10. At this time, since the ventilation resistance of the heat absorber 10 is increased, the air resistance of the first passage and the second passage changes in equilibrium. In short, the air volume of the air X decreases, and the air volume of the air Y increases. Then, the amount of air at the heat sink 10 is reduced, which further promotes frost formation. Therefore, in this low temperature state, the switch unit 19 is caused to perform a closing operation. In short, by closing the second dehumidification path, even if the blower 6 is still driven, the air Y does not flow into the second path of the heat exchanger 11. In this way, the suction force of the blower 6 can be fully used for suction in the first path, and the amount of air passing through the heat absorber 10 can be increased. Therefore, even when frost is started, the air flowing to the heat sink 10 is increased, that is, the progress of frost is suppressed, and the dehumidification operation for removing frost is further continued.

In this state, when the initial operating time (TS) has elapsed, for example, 25 minutes (step S4 in FIG. 7), the second temperature of the temperature of the detection heat sink 10 portion is determined. Whether the sensor 23 (ts) is equal to or lower than the second set temperature (t0, for example, 0.5 ° C). The initial operating time (TS) is the time after starting the "low temperature indicated operation".

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 shown in FIG. 6 “defrosting” (step in FIG. 7). S5, step S6).

Since this state is a state in which frost is expanded on the surface of the heat sink 10 due to continued low temperature operation, the control unit 21 performs a defrosting operation to eliminate frost.

In the defrosting operation, the control unit 21 stops the compressor 7 and further drives the blower 6 in a state where the switch unit 19 is turned off. (Step S6 in FIG. 7).

During the defrosting operation, the air X sucked only by the air inlet 3 through the blower 6 is blown to the heat sink 10 in a concentrated manner to eliminate frost on the surface of the heat sink 10. The operation time of the defrost operation is, for example, 10 minutes (Td: defrost accumulation time).

After the defrosting integration time (Td) has elapsed, the control unit 21 obtains the temperature of the second temperature sensor 23 (ts) that detects the temperature of the heat sink 10 portion. The control unit 21 detects that the temperature detected by the second temperature sensor 23 (ts) is equal to or greater than the second set temperature (t0, for example, 0.5 ° C) (step S8, step S9 in FIG. 7), or the set time Td (for example, 10) Minutes) to end the defrosting operation (step S7, step S9 in FIG. 7).

As described above, as shown in the "low temperature" operation, only by adjusting the air volume with the air flow adjustment unit, the progress of frost can be suppressed, and the frost can be eliminated. Perform dehumidification operation. In short, even if frosting occurs, dehumidification operation can still be performed and frosting can be eliminated to efficiently dehumidify.

(Third Embodiment)

Next, a dehumidifier according to a third embodiment will be described with reference to FIG. 8.

The characteristic point of the dehumidification device 52 of this embodiment is that, as shown in FIG. 8, in addition to the first dehumidification path through which air X flows and the second dehumidification path through air Y in the configuration shown in the first embodiment, There is also a third dehumidification path through which the air Z flows. Furthermore, the air Z is another part of the air sucked from the air suction port 2 or 3. Then, in this embodiment, one part of the air, the other part of the air, and the other part of the air are added together to form the total amount of air taken in by the dehumidifier 52. In other words, the other part of the air can be regarded as the part of the total amount of air sucked by the dehumidifying device 52 minus one part of the air and the other part of the air.

The other part of the air (air Z) sucked from the air inlet 2 or 3 by the blower 6 is blown out from the air outlet 4 to the main body casing without passing through the heat absorber 10 and the heat exchanger 11 and through the upper part 8a of the radiator 8 1 外.

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

Here, the heat radiator 8 projects more vertically upward than the upper end portion of the heat sink 10 or the upper end portion of the heat exchanger 11. This protruding portion corresponds to the upper portion 8 a and can be regarded as a part of the radiator 8 which is higher than the center in the height direction of the radiator 8. In addition, the vertical direction indicates that the dehumidifier 52 is generally installed. Above the operating state.

In this embodiment, the air Z passes through the upper portion 8 a of the radiator 8. The air X and the air Y pass through other parts of the heat radiator 8 located on the lower side than the upper portion 8a of the heat 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 heat radiator 8 is cooled, and as a result, the heat absorber 10 is cooled, and the dehumidification capability of the dehumidification device 52 can be improved.

Specifically, the refrigerant whose temperature has become high in the compressor 7 first flows into the upper portion 8 a side of the radiator 8. In summary, in the radiator 8, the upper portion 8 a has a higher temperature than the other portions of the radiator 8. Since the air Z cools the upper portion 8a of the heat radiator 8 having a higher temperature, the heat radiator 8 can be effectively cooled. As a result, the heat radiator 8 is cooled and the heat absorber 10 is cooled, so that the dehumidification capability of the dehumidifier 52 can be improved.

In addition, since the refrigerant which has become high in temperature due to the compressor 7 is vaporized, the compressor 7 is generally connected to the upper portion 8a of the radiator 8. Then, by cooling in the radiator 8, the refrigerant liquefies and moves vertically downward. Therefore, in this embodiment, the cooling effect of the radiator 8 is improved by passing the air Z through the upper portion 8a. However, structurally, the upper portion 8 a is not necessarily limited to being connected to the compressor 7. In this case, it is sufficient to pass the air Z through the connection portion on the compressor 7 side and the connection portion on the expander 9 side of the radiator 8 near the connection portion on the compressor 7 side. The connection part on the compressor 7 side has a higher temperature than the connection part on the expander 9 side. Therefore, by adopting the third dehumidification path, the connection part on the compressor 7 side of the radiator 8 is used to effectively cool the air Z. Radiator 8.

In addition, the additional air Z can increase the overall air volume (air x + air Y + air Z).

Furthermore, since the air Z cools the upper portion 8a of the radiator 8, the temperature rises when the air is blown out from the air outlet 4 to the outside of the main body case 1 when it is sucked from the air suction port 2 or 3.

As a result, compared with the configuration of the first embodiment, the temperature is higher, the humidity is lower, and air with a larger amount of air as a whole is blown out of the main body casing 1 through the air outlet 4.

Therefore, the use of a dehumidifying device, in the case of drying clothes in a living space, etc., can improve the drying effect.

Furthermore, a configuration is adopted in which 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 this embodiment, more specifically, the amount of air Z is preferably smaller than the amount of air Y flowing through the second passage of the heat exchanger 11. Specifically, the ventilation resistance of the air Z should be greater than the ventilation resistance of the air Y.

With this configuration, the amounts of the air X and the air Y that contribute to the dehumidification can be sufficiently ensured, so that the dehumidification capacity of the dehumidifier can be further effectively improved.

(Fourth embodiment)

Next, a dehumidifier according to a fourth embodiment will be described with reference to FIG. 9.

The characteristic point of the dehumidifier 53 in this embodiment is that, as shown in FIG. 9, the heat exchanger 11 configured as shown in the first embodiment adopts the upstream opening portion 18 a of the second passage to the air intake port 2 side. Inclined surface 55.

Further, in this embodiment, a circuit board 61 is provided above the heat exchanger 11 in the main body casing 1 as a control section for controlling the operation of the dehumidifier 53. The circuit board 61 is disposed near the heat exchanger 11.

The air Y sucked into the main body casing 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 flows into the heat exchanger 11 from the upstream opening portion 18a of the second passage. Then, it is blown out from the air outlet 4 to the outside of the main body casing 1 via the radiator 8 and the blower 6. In addition, the air X sucked into the main body casing 1 from the air suction port 3 by the blower 6 passes through the heat sink 10 and flows into the heat exchanger 11 through the upstream opening 17a of the first passage. After that, the air X flows out from the downstream opening 17b, and is blown out from the air outlet 4 through the radiator 8 and the blower 6 to the outside of the main body casing 1. At this time, heat is exchanged between the air X and the air Y in the heat exchanger 11, and condensation occurs in the second passage.

Here, in the air Y passing through the second passage, the air passing through the portion close to the radiator 8 has a small cooling effect due to the heat exchanger 11 and is hardly condensed.

In short, the air used to cool 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 through the upstream opening 17a on the heat sink 10 side, and flows out from the downstream opening 17b on the heat radiator 8 side. Therefore, the air passing through the second passage near the heat sink 10 is cooled first, and then the air passing through the second passage near the heat sink 8 is cooled.

Therefore, the air X flowing through the first passage first passes through the second passage The air close to the heat sink 10 is heat-exchanged, heated, and the air near the heat sink 8 passing through the second passage is cooled in the already heated state. Therefore, the temperature difference between the air passing through the second passage and the portion close to the radiator 8 becomes smaller, and the heat exchange rate becomes slower. Since the heat exchange speed is slow, it is not easy to cool, and it is difficult to cause condensation in the second passage.

In addition, when the air Y taken in from the air suction port 2 flows into the second passage of the heat exchanger 11, the flow direction changes sharply, so that the air volume is uneven in the second passage.

In short, the air Y taken in from the air suction port 2 provided on the back of the main body case 1 flows in the horizontal direction, but the upstream opening portion 18a of the second passage opens in the vertical direction (vertical upward), so the air The air flow was forced to turn. At this time, due to the inertia, the air flow of the air Y is uneven, and more air flows into the outside of the turn, that is, the portion of the second passage near the radiator 8. Then, since a large amount of air flows into the portion of the second passage close to the radiator 8, in order to cool the air to a dew point temperature to cause condensation, more cooling heat is required. However, as described above, since the air passing through the second passage near the radiator 8 is not easily cooled, it is difficult to cause condensation.

In contrast, in this embodiment, since the upstream opening portion 18a of the heat exchanger 11 is formed as an inclined surface 55 that is inclined toward the air intake port 2 side, it is easy to cool the portion close to the radiator 8 passing through the second passage. air. The details are described below.

The length in the longitudinal direction of the downstream-side opening portion 17 b of the first passage is extended toward the upper portion 8 a of the radiator 8. The height after the extension may be higher than the downstream end portion of the heat sink 10 (the upper end portion of the heat sink 10 in FIG. 9). As a result, the upstream-side opening portion 18a is inclined toward the air intake port 2 as a result. As a result, the passage length of the portion of the second passage close to the radiator becomes longer, and the time for passing through the heat exchanger 11 can be lengthened. Thereby, even if the temperature difference is small and the heat exchange speed is slow, the heat exchange can be performed for a longer time, and as a result, the heat exchange amount can be increased. Since the amount of heat exchange can be increased, the amount of cooling of the air passing through the second passage near the radiator 8 can be increased to increase the generation of condensation.

In addition, since the length in the longitudinal direction of the downstream-side opening portion 17b of the first passage is extended, and the upstream-side opening portion 18a is inclined toward the air intake port 2 side, it also easily flows into the portion of the second passage near the heat sink 10 to reduce the air volume. Uneven. In short, in the second passage, from the heat absorber 10 to the radiator 8, the passage length of the second passage becomes longer, and the ventilation pressure loss becomes larger. Therefore, the air Y is not easy to flow into the portion close to the radiator 8. On the other hand, since it is easy to flow into the portion close to the heat sink 10, the uneven amount of air flowing through the second passage is reduced. Due to the easing of the uneven air volume, the amount of air flowing through the second passage close to the radiator 8 is reduced, and the amount of cooling heat required to cool to the dew point temperature is reduced. Therefore, it is possible to increase the generation of condensation due to the air flowing through the second passage close to the radiator 8 portion.

As described above, it is possible to further increase the condensation generation caused by the air passing through the second passage of the heat exchanger 11 near the radiator 8 and further improve the dehumidification performance.

(Modification)

In the above-mentioned four embodiments, an example is shown in which the air intake is divided into two. In this embodiment, The amount of air is distributed using the air impedance of each channel. By doing so, it is not necessary to divide the air intake port into two, and the same effect can be obtained by using one air intake port.

In addition, when the amount of air passing through each passage is distributed using the opening area of the air suction opening without using air resistance, a plurality of air suction openings corresponding to each air quantity may be provided.

In the first embodiment and the third embodiment, the control unit is not described, but the first embodiment and the third embodiment may be provided with the control unit shown in the second embodiment. In this case, the control unit sends a control command to the compressor or the blower to make the dehumidifier operate. Of course, the control unit shown in the second embodiment may be embedded in the control unit shown in the fourth embodiment.

In addition, the above-mentioned four embodiments can be implemented at the same time as long as they are not contradictory. For example, to provide a dehumidifier with an air flow adjustment unit and a third dehumidification path.

The present invention can also be condensed in the heat exchanger part, so it is extremely useful as a dehumidifier with high dehumidification effect.

Claims (18)

A dehumidification device is provided with a main body casing having an air suction port and an air blowing outlet; and a dehumidification unit, which sequentially connects a compressor, a radiator, an expander, and a heat sink to a refrigeration cycle, and circulates air in the main body casing. Dehumidification; air blower to make the air outside the main body casing sucked in from the air suction port pass through the dehumidifying part, and then blow out from the air outlet to the main body casing; the heat exchanger is provided with a first passage, and The second channel which is independent of the first channel performs heat exchange between the air flowing through the first channel and the air flowing through the second channel; and the first dehumidification path is sucked into the air inlet from the air inlet through the air blower. Part of the air in the main body casing is blown out of the main body casing from the air outlet through the heat sink, the first passage of the heat exchanger, and the heat radiator; and the second dehumidification path will pass through the foregoing The air blower sucks the other part of the air in the main body casing from the air suction port through the second passage of the heat exchanger and the radiator to remove the air from the air. The outlet is blown to the outer casing body; and the use of flowing through the heat exchanger of the second air passage of an amount less than the amount of air flowing through the first passage of the exchanger constitutes. The dehumidifier according to claim 1, wherein the heat exchanger adopts a configuration in which the ventilation resistance of the second passage is larger than the ventilation resistance of the first passage. The dehumidifier according to claim 1 or 2, wherein the heat exchanger adopts a configuration in which the first passage and the second passage cross. The dehumidifier according to claim 3, wherein the heat exchanger has a rectangular parallelepiped shape, and a first passage opening portion is provided on an opposite long side, and a second passage opening portion is provided on an opposite short side. The dehumidifier according to claim 4, wherein the downstream-side opening portion for the second passage is an inclined surface that is inclined toward the radiator. The dehumidifier according to claim 4, wherein the upstream-side opening portion for the second passage is an inclined surface inclined toward the air intake port side. The dehumidifier according to claim 4, wherein the heat sink is installed on the air suction port side of the air passage from the air suction port to the air blowing port, then the heat exchanger is provided, and the heat radiator is provided. The dehumidifying device according to claim 5, wherein the heat absorber is provided on the air inlet side of the air passage from the air inlet to the air outlet, and then the heat exchanger and the heat radiator are provided. The dehumidifier according to claim 6, wherein the heat absorber is provided on the air suction port side of the air passage from the air suction port to the air blowing port, the heat exchanger is provided, and the heat radiator is provided. The dehumidifying device according to claim 1, wherein a water collecting part is provided below the heat sink and the heat exchanger in the main body casing. If the dehumidification device of item 1 is provided, it is provided with an air flow adjustment section to make the flow The air passing through the aforementioned second passage is increased or decreased. The dehumidifying device according to claim 11, wherein the air flow adjustment section is configured by a switch section that opens and closes the second path, and a drive section that drives the switch section. The dehumidifying device according to claim 12, wherein the switch unit is disposed between the air suction port and the second passage. For example, the dehumidifying device of claim 12 is provided with a first temperature sensor that detects the temperature of the driving unit, the blower, the compressor, and the air entering the air inlet; and the control unit, when the When the temperature detected by the first temperature sensor is equal to or lower than the first set temperature, the switch unit is caused to close by the drive unit. For example, the dehumidifying device of claim 14 is provided with a second temperature sensor to detect the temperature of the heat sink; the control unit is configured as follows: when the temperature detected by the first temperature sensor becomes the first setting, When the temperature is below the temperature, the blower and the compressor are driven in a state where the second path of the heat exchanger is closed by the switch unit; when the temperature detected by the second temperature sensor becomes the second setting When the temperature is below the temperature, the blower is driven and the compressor is stopped in a state where the second passage of the heat exchanger is closed by the switch unit. If the dehumidification device of item 1 is provided with a third dehumidification path, The blower blows another part of the air sucked into the main body casing from the air suction port into the main body casing without passing through the heat absorber and the heat exchanger and through the heat radiator to the outside of the main body casing. The dehumidifying device according to claim 16 has a configuration in which the third dehumidifying path passes through the connection portion on the compressor side of the radiator. For example, the dehumidifying device of claim 16 has a structure in which the amount of air flowing through the third dehumidifying path is smaller than the amount of air flowing through the second path.