JP2001215030A - Dehumidifying apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a dehumidifying apparatus for continuously supplying dry air with absolute humidity of 4 g/kgDA or lower. SOLUTION: A dehumidifying apparatus comprises a heat pump which includes a water absorption apparatus in which water in processing air is absorbed and is dissolved and regenerated, a condenser for heating regenerated air on an upstream side of the water adsorption apparatus by condensing a refrigerant, an evaporator for cooling regenerated air to a temperature of a due point or lower on a downstream side of the water adsorption apparatus by evaporating a refrigerant, a booster for boosting and feeding the refrigerant evaporated in the evaporator, and a heat pump for heat exchanging the regenerated air flowing between the water adsorption apparatus and the evaporator and the regenerated air flowing between the evaporator and the condenser. Since moisture in the processing air is removed by the water adsorption apparatus, air with absolute humidity not higher than 4 g/kgDA at a due point not higher than the freezing point.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

TECHNICAL FIELD The present invention relates to a dehumidifier,
In particular, the present invention relates to a dehumidifier having a high dehumidifying ability.

[0002]

2. Description of the Related Art Conventionally, as shown in FIG. 10, a compressor 1 for compressing a refrigerant C, a condenser 2 for condensing the compressed refrigerant C and heating the processing air A, and an expansion valve for condensing the refrigerant C 5
The dehumidifier 11 was equipped with an evaporator 3 for reducing the pressure and reducing the temperature of the treated air A to a temperature equal to or lower than the dew point. The evaporator 3 cools the processing air A from the air conditioning space 10 below the dew point, removes moisture in the processing air A, heats the processing air A cooled below the dew point with the condenser 2, Had been supplied. In the dehumidifier 11, the compressor 1, the condenser 2, the expansion valve 5, and the evaporator 3 constitute a heat pump HP. The heat pump HP is an evaporator 3
From the processing air A flowing through the condenser 2 to the processing air A flowing through the condenser 2.

[0003]

SUMMARY OF THE INVENTION
The dehumidifier 11 equipped with the heat pump HP could not supply dry air of 4 g / kg DA or less in absolute humidity. In this case, since the operating temperature of the evaporator 3 of the heat pump HP is lower than the freezing point, the dehumidified moisture becomes ice on the heat transfer surface to land on the heat transfer surface and hinders the heat transfer, making continuous operation impossible. That's why.

[0004] Therefore, the present invention does not allow the dehumidified moisture to land on the heat transfer surface of the evaporator of the heat pump as ice even when the air is dehumidified, and continuously supplies dried air having an absolute humidity of 4 g / kg DA or less. It is an object of the present invention to provide a dehumidifier capable of supplying the dehumidifier.

[0005]

In order to achieve the above object, a dehumidifier according to the first aspect of the present invention, as shown in FIG. Moisture adsorption device 10 that is regenerated by desorbing water
3; a condenser 220 for heating the regeneration air B upstream of the moisture adsorption device 103 by condensing the refrigerant C, and a dew point below the dew point on the downstream side of the moisture adsorption device 103 by evaporating the refrigerant C Evaporator 2 to cool to the temperature of
10, a booster 260 that boosts the refrigerant C evaporated in the evaporator 210 and sends it to the condenser 220, a regeneration air B flowing between the moisture adsorption device 103 and the evaporator 210, and an evaporator 21.
Heat pump HP1 having a heat exchanger 300 for exchanging heat with the regeneration air B flowing between the condenser air and the condenser 220.
The regeneration air B is configured to be circulated and used.

[0006] With this configuration, since the condenser, the evaporator, and the heat exchanger are provided, the regeneration air is heated by the condenser, the moisture content is increased by regenerating the moisture adsorption device, and the heat exchange is performed. The water is cooled by the evaporator, the water content is reduced by the condensation of water by the evaporator, and the heat is circulated by the heat exchanger. In the regenerated air, part of the moisture is condensed by cooling by the heat exchanger, and the content of the moisture may be reduced. Before being cooled by the evaporator, it is cooled by the heat exchanger (pre-cooling), and after being cooled by the evaporator, it is heated by the heat exchanger (pre-heating), so that a low sensible heat ratio operation can be performed.

[0007] Further, the moisture of the treated air is adsorbed by the moisture adsorbing device, so that the humidity of the treated air is greatly reduced.
Dry air can be supplied. Recycling of the regeneration air means that the regeneration air after regenerating the desiccant of the moisture adsorbing device, for example, the desiccant rotor, is not exhausted to the atmosphere as it is (partially may be exhausted), and most of it is re-exposed. It means that it is configured to flow through a circulation circuit to be used as regeneration air.

[0008] In the heat exchanger, evaporation and condensation of the refrigerant are typically performed at a pressure intermediate between the condensing pressure in the condenser and the evaporating pressure in the evaporator.

According to a second aspect of the present invention, in the dehumidifying apparatus according to the first aspect, the heat exchanger includes a group of small tubes connecting the condenser and the evaporator; The regeneration air that is configured to guide the refrigerant condensed in the condenser to the evaporator, and that flows between the moisture adsorption device and the evaporator, and that flows between the evaporator and the condenser. It is characterized in that it is configured to alternately contact the regeneration air.

[0010] With this configuration, the group of thin tubes through which the refrigerant is introduced alternately comes into contact with the regeneration air flowing between the moisture adsorber and the evaporator and the regeneration air flowing between the evaporator and the condenser. Therefore, heat can be exchanged between the regenerated air via the refrigerant. The connection here is a concept including indirect connection via a pipe, a pipe joint or the like.

According to a third aspect of the present invention, in the dehumidifying apparatus according to the second aspect, the heat exchanger includes a first section through which the regenerated air flows between the moisture adsorbing apparatus and the evaporator. And a second section through which the regeneration air flows between the evaporator and the condenser.
After passing through the first section and the second section alternately and repeatedly, and then connected to the evaporator through a second throttle. And

With this configuration, the first stop and the second stop
During the passage of the refrigerant through the first throttle and the passage of the second throttle, a pressure drop of the refrigerant occurs, and the evaporation of the refrigerant passing through the first section and the second Is condensed at a pressure intermediate between the condensation pressure of the refrigerant in the condenser and the evaporation pressure of the refrigerant in the evaporator. Thus, the heat exchanger acts as an economizer,
The operating coefficient of the heat pump is improved.

According to a fourth aspect of the present invention, in the dehumidifying apparatus according to the third aspect, the first section and the second section are such that regenerated air flowing through each section faces each other. A plurality of first section penetrations in the first section and the second section within a first plane substantially orthogonal to the flow of the regenerating air; A second partition penetrating portion, wherein at least one pair of the first partition penetrating portion and the second partition penetrating portion are provided in a second plane substantially orthogonal to the flow of the regenerating air different from the first plane. And an intermediate stop at a position moving from the first plane to the second plane.

With this configuration, from the viewpoint of the heat exchange between the regenerated air, the flow is counter-current heat exchange.
High heat exchange efficiency can be achieved. A first section having at least one pair of a first section penetrating section and a second section penetrating section,
A pair of refrigerant paths, and at least one pair of first refrigerant passages in a second plane substantially orthogonal to the flow of regeneration air different from the first plane.
And a pair of refrigerant passages, so that the heat exchanger as a whole can be made compact and compact. In addition, since an intermediate throttle is provided at a position where the inside of the first plane moves into the second plane, the pressure of evaporation or condensation of the first and second section penetration portions in the second plane is reduced by the first plane. Can be set to a value lower than the pressure of the evaporation or condensation of the first and second section penetration portions, so that the heat exchange between the regenerated air flowing through each section can be close to the counterflow heat exchange, Heat exchange efficiency can be increased. The shapes of the first surface and the second surface are typically rectangular planes.

[0015]

Embodiments of the present invention will be described below with reference to the drawings. In the drawings, the same or corresponding members are denoted by the same or similar reference numerals, and duplicate description is omitted.

FIG. 1 is a flow chart of a dehumidifying apparatus 21 according to a first embodiment of the present invention. This dehumidifier 21
Is a dehumidifier 21 that circulates the regeneration air B to regenerate the desiccant and dehumidifies the processing air A using the desiccant. FIG. 2 is a schematic front sectional view of the dehumidifier 21 of FIG. FIG. 3 is a refrigerant Mollier diagram of the heat pump HP1 included in the dehumidifier 21 of FIG. 1, and FIG. 4 is a humid air diagram of the dehumidifier 21 of FIG.

Referring to FIG. 1, the structure of a dehumidifier 21 according to a first embodiment will be described. This dehumidifier 21
The regenerated air B after regenerating the desiccant is cooled below its dew point temperature to recover the moisture in the regenerated air B as dew condensation water. The regenerated desiccant dehumidifies the processing air A, and the processing air A is supplied. The air conditioning space 101 is maintained at a low humidity.

In the figure, the processing air-related equipment configuration will be described along the path of the processing air A from the air-conditioned space 101. First, a path 107 connected to the air-conditioned space 101, a blower 102 for circulating the processing air A, a path 108, a desiccant rotor filled with a desiccant for absorbing moisture of the processing air A passing therethrough and lowering the humidity of the processing air A The processing air A is arranged to return to the air-conditioned space 101 from the path 109 in this order. Each of the paths 107 to 109 corresponds to each of the paths 10
The devices described before 7 to 109 are connected to the devices described later. The desiccant rotor 103 is the moisture adsorption device of the present invention.

Next, the configuration of the equipment related to the regeneration air will be described along the path of the regeneration air B. The second section 320 of the heat exchanger 300 acting as an economizer, path 124,
Condenser 220, path 125, desiccant rotor 10 filled with desiccant regenerated by passing regenerated air B
3, path 126, first section 310 of heat exchanger 300,
Path 127, blower 14 for circulating regeneration air B
0, a path 128, an evaporator 210 for cooling the regenerated air B to a temperature lower than its dew point and recovering water in the regenerated air B as dew condensation water, and a path 129. From 129, it is configured to return to the second section 320 of the heat exchanger 300 for further circulation.
Therefore, it is not necessary to exhaust the regenerated air B to the outside, and since high-humidity exhaust is not discharged indoors (in the air-conditioned space 101), the dehumidifier is moved regardless of the installation location of the dehumidifier 21. It can also be an expression.

Each of the paths 124 to 129 is the same as the device described above before each of the paths 124 to 129,
Connect to the equipment described later. The evaporator 210
The moisture in the regeneration air B condensed by the water is collected by the drain pan 451 and accumulated in the drain tank 450.

Next, the equipment configuration of the heat pump HP1 will be described along the path of the refrigerant C. Evaporator 210 for heating and evaporating refrigerant C, path 201, compressor 260 as a booster of the present invention for compressing refrigerant C evaporated and gasified in evaporator 210, path 202, cooling refrigerant C A condenser 220 for condensing and condensing, a path 203 containing a throttle 330,
Regenerative air B flowing through the first section 310 of the heat exchanger 300
Section 252 for heating the regenerated air B flowing through the second section 320 of the heat exchanger 300, the path 204 containing the throttle 250, and the refrigerant C evaporate again. It is configured to return to the vessel 210. Each of the paths 201 to 204
In the above description, the device described before each of the paths 201 to 204 is connected to the device described later.

The desiccant rotor 103 is formed as a thick disk-shaped rotor that rotates around the rotation axis AX, and the rotor is filled with a desiccant (not shown in FIG. 1) with a gap through which gas can pass. Have been.
For example, a tubular drying element (not shown in FIG. 1)
Are bundled so that their central axes are parallel to the rotation axis AX. This rotor rotates in one direction around the rotation axis AX, and the processing air A and the regeneration air B
It is configured to flow in parallel to X and flow out of each. Each drying element is arranged so as to alternately contact the processing air A and the regeneration air B as the desiccant rotor 103 rotates. Generally, the processing air A and the regeneration air B are configured so as to flow in a substantially half area of the circular desiccant rotor 103 in a counterflow manner in parallel with the rotation axis AX.

The desiccant is preferably filled in the above-mentioned tubular drying element. Desiccant rotor 103
Is configured such that the processing air A and the regeneration air B flow in the thickness direction of the disk-shaped rotor.

Next, the configuration of the heat exchanger 300 will be described with reference to FIG. The heat exchanger 300 is a heat exchanger 300 that indirectly exchanges heat via the refrigerant C between the regenerated air B before and after flowing into the evaporator 210. Heat exchanger 3
00 denotes a plurality of heat exchange tubes as refrigerant paths or thin tubes in a plurality of different planes PA, PB, PC,... Which are orthogonal to the plane of the drawing and orthogonal to the flow of the regeneration air B. They are arranged almost in parallel. In this figure, only one tube is shown in each plane for convenience of illustration.

The heat exchanger 300 has a first section 310 through which the regeneration air B before passing through the evaporator 210 flows, and a second section 3 through which the regeneration air B after passing through the evaporator 210 flows.
20 form separate rectangular parallelepiped spaces. In both compartments, a partition 301 and a partition 302 are provided adjacent to each other.
02 is provided.

As another form, the heat exchanger 300 divides one rectangular parallelepiped space by one partition, and the heat exchange tube penetrates the partition to alternate between the first section and the second section. You may be comprised so that it may penetrate.

Regenerated air B exiting the desiccant rotor 103
From the right through the path 126 through the heat exchanger 300
Of the first section 310 and exits through the path 127 from the left. On the other hand, the regenerated air B cooled to the dew point temperature or lower and reduced in absolute humidity through the evaporator 210 is supplied to the second section 320 of the heat exchanger 300 through the path 129 from the left in the figure, and from the right in the path. Go out through 124.

As shown, the heat exchange tube is
The first partition 310 and the second partition 320 are provided so as to penetrate the partition 301 and the partition 302 which partition the partitions. For example, a heat exchange tube disposed in the plane PA is provided with a portion penetrating the first section 310 as an evaporating section 251A (hereinafter, when a plurality of evaporating sections do not need to be individually discussed, they are simply referred to as the evaporating section 251). And a portion penetrating through the second section 320 is referred to as a condensing section 252A as a second refrigerant path (hereinafter simply referred to as a condensing section 252 when it is not necessary to separately discuss a plurality of condensing sections). Here, the evaporating section 251A and the condensing section 252A are a pair of a first section penetrating section and a second section penetrating section, and constitute a refrigerant passage.

Further, in the heat exchange tube arranged in the plane PB, the evaporating section, which is a portion penetrating the first section 310, is set to 251B. Also, the second section 3
The evaporating section 2 which is a portion penetrating through
A portion forming a pair of refrigerant paths with 51B is a condensing section 252B as a second refrigerant path. Hereinafter, a refrigerant path is also formed for the plane PCs in the same manner as for the plane PB.

As shown in the figure, the evaporating section 251A and the condensing section 252A form a pair and are formed as an integral path by one tube. Therefore,
Combined with the fact that the first section 310 and the second section 320 are provided adjacent to each other with the two partition walls 301 and 302 interposed therebetween, the heat exchanger 300 can be formed to be small and compact as a whole. .

In the form of the heat exchanger shown in the figure, the evaporating section as the first section penetrating portion is 251A, 2B from the right in the figure.
51B, 251C,..., And the condensing section as the second section penetration portion is also 252A from the right in the figure,
252B, 252C,...

As further shown, the condensing section 25
The end of 2A (the end opposite to the partition 302) and the end of the condensation section 252B (the end opposite to the partition 302) are connected by a U-tube (YouTube). Further, the end of the evaporation section 251B and the evaporation section 2
The end of 51C is similarly connected by a U-tube.

Therefore, the refrigerant C flowing from the evaporating section 251A to the condensing section 252A as a whole in one direction is guided to the condensing section 252B by the U-tube, flows therefrom to the evaporating section 251B, and flows to the evaporating section 251C by the U-tube. It is configured as follows. In this way, the refrigerant path including the evaporating section and the condensing section alternately and repeatedly passes through the first section 310 and the second section 320. In other words, the refrigerant path forms a meandering group of small tubes. The thin tube group passes through the first section 310 and the second section 320 while meandering, and alternately comes into contact with the high-temperature regeneration air B and the low-temperature regeneration air B.

Next, the flow of the refrigerant C between the devices will be described with reference to FIG.

In the figure, a refrigerant gas C compressed by a refrigerant compressor 260 is guided to a condenser 220 via a refrigerant gas pipe 202 connected to a discharge port of the compressor 260. The refrigerant gas C compressed by the compressor 260 is cooled and condensed by the regeneration air B serving as cooling air immediately before flowing into the desiccant rotor 103, and the refrigerant C heats the regeneration air B.

The refrigerant outlet of the condenser 220 is connected to the heat exchanger 30
0 refrigerant passage 203 at the entrance of the evaporating section 251A.
A throttle 330 is provided in the middle of the refrigerant path 203 near the entrance of the evaporating section 251A.

The liquid refrigerant C that has exited the condenser 220 is
At 0, the pressure is reduced, expanded, and a part of the liquid refrigerant C evaporates (flashes). The refrigerant C in which the liquid and gas are mixed reaches the evaporating section 251A, where the liquid refrigerant C flows so as to wet the inner wall of the tube of the evaporating section 251A, and is heated by the regenerated air B immediately after flowing out of the desiccant rotor 103. Then, the regeneration air B flowing through the first section 310 is cooled (precooled). The regeneration air B is the regeneration air B before flowing into the evaporator 210.

Evaporation section 251A and condensation section 252A are a series of tubes. That is, since the refrigerant gas C is evaporated as an integral path,
(And the refrigerant liquid C that did not evaporate)
Flow into 52A. Then, the regeneration gas B flowing through the second section 320, that is, the regeneration air B cooled and dehumidified by the evaporator 210 and having a lower temperature than before flowing into the evaporator 210 is heated (preheated), and the refrigerant gas C itself is heated. Is deprived of heat and condenses.

As described above, the heat exchanger 300 is provided in the first plane PA with the evaporation section, which is a refrigerant path passing through the first section 310, and the condensation, which is a refrigerant path passing through the second section 320. A refrigerant section having a section (at least one pair, for example, 251A and 252A) and being in a second plane PB, the condenser section being a refrigerant path through the second section 320 and a refrigerant path through the first section 310. (At least one pair, for example, 252B and 251B).

The last condensing section 2 of the heat exchanger 300
The outlet side of 52E is connected to the evaporator 2 by refrigerant liquid piping 204.
An expansion valve 250 is installed in the refrigerant pipe 204 as a throttle.

Refrigerant liquid C condensed in condensing section 252
The evaporator 210 is decompressed and expanded by the throttle 250 to reduce the temperature, enter the evaporator 210, evaporate, and cool the regenerated air B by the heat of evaporation. As the throttles 330 and 250, for example, orifices, capillary tubes, expansion valves, and the like are used.

Refrigerant C evaporated and gasified by evaporator 210
Is guided to the suction side of the refrigerant compressor 260 through the path 201, and the above cycle is repeated.

In the figure, the behavior of the refrigerant C in the evaporating section and the condensing section of the heat exchanger 300 will be described. First, a refrigerant C containing a liquid phase and a gas phase flows into the evaporating section 251A. The refrigerant C pre-cools the regenerated air B while flowing through the evaporating section 251A, and flows into the condensing section 252A while heating and increasing the gas phase. The condensing section 252A heats the regenerated air B having a lower temperature than the regenerated air B in the evaporating section 251A by being cooled and dehumidified. Flow into section 252B. While the refrigerant C flows through the condensing section 252B,
The heat is further removed by the low-temperature regenerated air B, and the gas-phase refrigerant C is further condensed. Then, it flows into the next evaporation section 251B.

As described above, in the heat exchanger 300, the refrigerant C
Flows through the refrigerant path while undergoing a phase change between a gas phase and a liquid phase.
In this way, heat is exchanged between the regeneration air B before being cooled by the evaporator 210 and the regeneration air B cooled by the evaporator 210 to reduce the absolute humidity.

In the present dehumidifier 21, the heat exchanger 300 is used as a pre-cooling / pre-heating heat exchanger, and the working fluid of the heat exchanger 300 and the working fluid of the heat pump HP1 are the same, so that the refrigerant charging process is shared. Manufacturing costs and maintenance costs are low. In addition, the pre-cooling / pre-heating heat exchanger can be manufactured as a single unit, and does not require the internal wick of the heat pipe, and can be manufactured using ordinary air / refrigerant heat exchanger coil production equipment without an internal wick. Therefore, the manufacturing cost is low.

In the dehumidifier 21, the heat pump HP1
, The desiccant regeneration and moisture removal from the regeneration air are performed simultaneously, and the preheating of the regeneration air B before regeneration and the precooling of the regeneration air B after regeneration are performed using the internal working medium. Therefore, the device is simple, and most of the cooling capacity of the heat pump can be used for condensing moisture in the air, so that the dehumidifying capacity is high.

In the case of cooling and dehumidifying air, if the air is cooled to the dew point as it is, a large amount of cooling is required. Therefore, a considerable part of the cooling effect of the heat pump is consumed for that purpose, and the dehumidifying capacity per power consumption (dehumidifying performance) is low. Therefore, an air / air heat exchanger 300 is provided before and after the evaporator 210 to perform pre-cooling and reheating (pre-heating) of the regeneration air B, thereby reducing the sensible heat ratio and reducing the amount of cooling to the dew point.

The dehumidifier 21 has a high dehumidifying ability and, in addition, recovers heat for cooling to the dew point and can use it as heat for heating the regenerated air. be able to. Therefore, the amount of heat required is smaller than the amount of heat required by the conventional electric heater, and the heat pump HP1 has high energy efficiency.
Low power consumption.

Referring to FIG. 2, dehumidifier 2 described above
An example of mechanical arrangement 1 will be described. In the figure, devices constituting the device are housed in a cabinet 700. The cabinet 700 is formed as, for example, a rectangular parallelepiped housing made of a thin steel plate, and is hermetically divided into an upper region 700A and a lower region 700B vertically arranged by a horizontal planar partition plate 701 and a lower region 700B. ing. The upper region 700A is a processing air chamber 702 through which the processing air A flows from the left end to the right end in the drawing, and the lower region 700B is mainly a regeneration air chamber 703, and the inside of the regeneration air chamber 703 is regenerated as described later. Air B circulates. A space for accommodating the compressor 260 and the drain tank 450 is secured in the lower region 700B, avoiding the regeneration air chamber 703. As the partition plate 701, for example, a thin steel plate forming the cabinet 700 may be used.

First, the arrangement of devices in the processing air chamber 702 will be described. Left side 7 of cabinet 700 in the figure
An intake port 104 is opened at the uppermost portion in the vertical direction of 04A, and the intake port 104 takes in the processing air A in the air-conditioned space 101 (see FIG. 1). The intake port 104 is an opening of the processing air chamber 702, and the sucked processing air A flows through the processing air chamber 702. A filter 501 is provided near the intake port 104 in the processing air chamber 702 so that dust in the air-conditioned space 101 is not brought into the apparatus. Filter 501
A blower 102 is installed inside the
04 through the filter 501 and the processing air chamber 702
The processing air A flowing into the inside is sucked into the blower 102. A path 107 is formed between the intake port 104 and the blower 102. The processing air A is blown by the blower 102.
Flows through the processing air chamber 702.

Process air A discharged from blower 102
Flows through the path 108 and flows into the upper half of the desiccant rotor 103 from the horizontal direction.
The desiccant is dehumidified. The processing air A flowing horizontally from the upper half of the desiccant rotor 103 passes through the path 1
09, the right side surface 70 of the cabinet 700 in the drawing.
The processing air chamber 702 (that is, the cabinet 700) exits from the discharge port 110 that is open at the top in the vertical direction of 4B, and returns to the air-conditioned space 101 to be supplied with air.

The desiccant rotor 103 has an opening 70 formed in the partition plate 701 with the rotation axis AX directed in the horizontal direction.
6, the upper half of the semicircular shape is disposed in the processing air chamber 702, and the lower half of the semicircular shape is disposed in the later-described upper section 703 </ b> A of the regeneration air chamber 703. An electric motor 105 serving as a driving machine is arranged near the desiccant rotor 103 in a later-described upper section 703A of the regenerating air chamber 703 with a rotation axis being horizontal. The electric motor 105 and the desiccant rotor 103 are connected via a chain 131, and the rotation of the electric motor 105 is transmitted to the desiccant rotor 103, and the desiccant rotor 103 is driven for 15 to 20 hr ^-1.
It rotates at the number of rotations. Since the desiccant rotor 103 is arranged with the rotation axis AX oriented in the horizontal direction, the cabinet 70
The horizontal length of 0 can be made short and compact.

The height of the processing air chamber 702 is formed slightly larger than the radius of the desiccant rotor 103, and the height of the regeneration air chamber 703 is formed slightly smaller than twice the radius of the desiccant rotor 103. The regeneration air chamber 703 is provided with a horizontal planar partition plate 707 separated from the partition plate 701 by a distance slightly larger than the radius of the desiccant rotor 103 to the lower side, and the regeneration air chamber 703 is separated by the partition plate 707. It is divided into two sections 703A and B in the vertical direction. Openings 70 are provided at both ends of the partition plate 707.
5A and 5B are formed so that the regenerated air B circulates through upper and lower two sections 703A and B through the openings 705A and B.

Next, the arrangement of devices in the regeneration air chamber 703 will be described. Area 703A above regeneration air chamber 703
A filter 502 is installed on the right side of the drawing to remove dust from the regenerated air B that passes through the opening 705B on the right side of the figure, rises from the lower area 703B, turns in the horizontal direction, and flows. On the left side of the filter 502 in the figure, a condenser 220 formed in a coil shape is installed.
2 passes through the condenser 220 and is heated. The regeneration air B passing through the condenser 220 and passing through the path 125 flows from the horizontal direction into the lower half of the desiccant rotor 103 to regenerate the desiccant. The regenerated air B flowing horizontally from the lower half of the desiccant rotor 103 flows into the first section 310 of the heat exchanger 300 via the path 126 and is precooled.

Here, the arrangement of the heat exchanger 300 will be described. The heat exchanger 300 penetrates through the opening 708 formed in the partition plate 707, and the upper area 703A of the regeneration air chamber 703.
And the first section 310 of the heat exchanger 300 is stored in the upper section 703A.
The second section 320 of 0 is stored in the lower section 703B.

The regeneration air B flowing out of the first section 310 of the heat exchanger 300 is sucked into the blower 140 which circulates the regeneration air B in the regeneration air chamber 703 via the path 127. The regenerated air B discharged from the blower 140 passes through an extremely short path 128, passes through the coil-shaped evaporator 200, is cooled, and while flowing through the path 129, changes the direction of the flow to just below. , Opening 70 on the left side in the figure
Pass 5A. The regeneration air B passing through the left opening 705A changes the flow direction to the horizontal direction, and
03 flows horizontally in the lower section 703B, flows into the second section 320 of the heat exchanger 300, and is preheated. The drain tank 450 and the compressor 260 are provided in the regeneration air chamber 7.
03 is arranged on the front side in the horizontal direction in the figure. Regenerated air B flowing out of the second section 320 of the heat exchanger 300
Flows through the path 124, changes the direction of the flow to just above, passes through the opening 705B on the right side in the figure, changes the direction of the flow to the horizontal direction, reaches the filter 502, and thereafter repeats and circulates the same flow .

Next, the heat pump HP1 through which the refrigerant C flows
The arrangement of each device that constitutes the device will be described. The compressor 260 and the drain tank 450 are arranged below the partition plate 707 so as to avoid the area 703B below the regeneration air chamber. When viewed from the front in the figure, the compressor 260 has the desiccant rotor 10
3, and the drain tank 450 is disposed almost directly below the evaporator 210. Route 201-20
4 are connected to each other as shown in FIG.

In the above description, the processing air A is arranged so as to flow in the horizontal direction, and the equipment is arranged so that the regeneration air B mainly flows in the horizontal direction and flows slightly in the vertical direction to circulate. A may be arranged so that A flows in the vertical direction, and the equipment may be arranged so that the regeneration air B mainly flows in the vertical direction and slightly flows in the horizontal direction to circulate.

Next, referring to FIG. 3, heat pump HP1
The operation of will be described. FIG. 3 is a Mollier diagram when FC134a is used as the refrigerant H. Note that FIG. 1 is referred to for devices. In this diagram, the horizontal axis is enthalpy and the vertical axis is pressure. In addition, as the refrigerant C suitable for the heat pump and the dehumidifier 21 (see FIG. 1) of the present invention, HFC
407C and HFC410A. These refrigerants C
The operating pressure range shifts to a higher pressure side than the HFC 134a.

In the figure, the point a is the state of the refrigerant outlet of the evaporator 210 of FIG. 1 and is in the state of saturated gas. Pressure is 0.3
0MPa, temperature 1 ° C, enthalpy 399.2kJ /
kg. The state where this gas is sucked and compressed by the compressor 260, that is, the state at the discharge port of the compressor 260 is point b.
Indicated by In this state, the pressure is 1.89 MPa and the state is a superheated gas.

The refrigerant gas C is cooled in the condenser 220 and reaches a point c on the Mollier diagram. This point is a saturated gas state, the pressure is 1.89 MPa, and the temperature is 65 ° C. Under this pressure, it is further cooled and condensed to reach point d. This point is a saturated liquid state, the pressure and temperature are the same as point c, and the enthalpy is 295.8 kJ / kg.

The refrigerant liquid C is decompressed by the throttle 330 and flows into the evaporating section 251A of the heat exchanger 300. On the Mollier diagram, it is indicated by a point e. The pressure is an intermediate pressure of the present invention, and is 0.30 MPa and 1.
This is an intermediate value from 89 MPa. Here, a part of the liquid is evaporated and the liquid and the gas are mixed.

In the evaporating section 251A, the refrigerant liquid C evaporates under the intermediate pressure and reaches a point f1 between the saturated liquid line and the saturated gas line at the same pressure. Here, a part of the liquid has been evaporated, but the refrigerant liquid C remains considerably.

The refrigerant C in the state indicated by the point f1 flows into the condensation section 252A. Condensing section 252A
Then, the refrigerant C is deprived of heat by the low-temperature regeneration air B flowing through the second section 320, and reaches the point g1.

The refrigerant C in the state of the point g1 flows into the evaporating section 251B, where the heat is deprived and the liquid phase is increased, reaches the point f2, and flows into the condensing section 252B. Here, the liquid phase is increased to reach point g2. Similarly, repeat evaporation and condensation in the evaporation section and condensation section,
In the Mollier diagram of FIG. 3, the condensation section 252B is omitted from the expansion valve 25,
It is shown as connected to 0.

The point g2 is on the saturated liquid line in the Mollier diagram. The temperature is 15 ° C and the enthalpy is 220.5 kJ / kg
It is. The refrigerant liquid C at the point g2 is condensed at a temperature of 15
The pressure was reduced to a saturation pressure of 0.30 MPa
To reach. The refrigerant C at this point j reaches the evaporator 210 as a mixture of the refrigerant liquid C and gas at 1 ° C., where it takes heat from the processing air A, evaporates, and saturates the state at the point a on the Mollier diagram. It becomes gas and is sucked into the compressor 260 again, and the above cycle is repeated.

As described above, in the heat exchanger 300, the refrigerant C flows from the point e to the point f in the evaporating section 251.
1 or a change in the state of evaporation, such as from g1 to f2, in the condensing section 252, from the point f1 to the point g.
1 or the state of condensation changes from point f2 to point g2, and because it is evaporation heat transfer and condensation heat transfer,
Very high heat transfer rate and high heat exchange efficiency.

When the heat exchanger 300 is not provided as the compression heat pump HP1 including the compressor 260, the condenser 220, the throttles 330 and 250, and the evaporator 210, the refrigerant C in the state of the point d in the condenser 220 Is returned to the evaporator 210 via the restrictor 250.
Enthalpy difference available in is 399.2-295.8 =
103.4kJ / kg but heat exchanger 3
Heat pump HP1 used in the present embodiment provided with a heat pump 00
In the case of, 399.2-220.5 = 178.7 kJ /
kg, and the amount of gas circulating through the compressor 260 for the same cooling load, and thus the required power, can be reduced by as much as 42%. That is, the same operation as in the subcool cycle can be provided.

Due to the economizer effect of the heat pump,
Since the refrigerant enthalpy at the inlet of the evaporator 210 is small and the refrigerant has a high refrigeration effect per unit flow rate, the dehumidification effect and the energy efficiency are high.

The operation of the dehumidifier 21 having the heat pump HP1 will be described with reference to the psychrometric chart shown in FIG. 4 and the configuration as appropriate with reference to FIG. In FIG. 4, the state of air in each part is indicated by alphabetical symbols K, L, P, R and the like. This symbol corresponds to the circled alphabet in the flow diagram of FIG. 4 can be applied to the dehumidifiers of the second and third embodiments to be described later.

In the figure, the processing air A from the air-conditioned space 101
(State K) indicates that the blower 1
The air is blown into the desiccant rotor 103 through the path 108. The treated air A dried by absorbing moisture with the desiccant rotor lowers the absolute humidity to 2 g / kg DA and raises the dry bulb temperature (state L). Process air A is then routed 109
And returns to the air-conditioned space 101. DA in the unit of absolute humidity indicates dry air.

On the other hand, an absolute humidity of 5 g /
The regeneration air B (state P) at kgDA, dry-bulb temperature of 5 ° C. is passed through a path 129 to the second section 320 of the heat exchanger 300.
, Where it is heated to some extent by the refrigerant C condensed in the condensing section 252, and the dry bulb temperature is raised while maintaining the absolute humidity constant (intermediate temperature between 5 ° C. and 60 ° C.) (state R). This can be called pre-heating because it is pre-heating before being heated by the condenser 220.

The preheated regeneration air B is introduced into the condenser 220 through the passage 124. The regeneration air B is heated by the condenser 220, and further raises the dry bulb temperature to 60 ° C. while keeping the absolute humidity constant (state T). The regenerated air B is further fed through a path 125 to the desiccant rotor 103, where it dewaters the desiccant (not shown in FIG. 1) in the drying element and regenerates it. While increasing the pressure to kg DA, the dry bulb temperature is lowered by the heat of attaching and detaching the moisture of the desiccant (state U).

Regenerated air B exiting desiccant rotor 103
Is sent to the first section 310 of the heat exchanger 300 through the path 126, where it is cooled to some extent by the refrigerant C evaporating in the evaporating section 251 and the dry-bulb temperature is lowered while the absolute humidity is kept constant (state V). . This is evaporator 2
Since it is preliminary cooling before cooling to below the dew point temperature at 10, it can be called pre-cooling. Regenerated air B is in path 12
Path 7 drawn by blower 140 through path 128
It is exhaled. The discharged regenerated air B
8, is sent to the evaporator 210, is dehumidified and cooled to the dew point temperature or lower by the evaporator 210, and has an absolute humidity of 5 g / kg.
DA and the dry bulb temperature to 5 ° C. (state P). The regenerated air B exiting the evaporator 210 repeats the same cycle.

In the heat exchanger 300, the evaporating section 25
1, the regeneration air B is precooled by the evaporation of the refrigerant C, and the regeneration air B is heated by the condensation of the refrigerant C in the condensation section 252. And the refrigerant C evaporated in the evaporating section 251
Condenses in the condensing section 252. As described above, heat exchange between the regenerated air B before and after being cooled by the evaporator 210 is indirectly performed by the same evaporation and condensation of the refrigerant C.

Here, in the cycle on the air side shown in the psychrometric chart of FIG. 3, the heat quantity ΔQ obtained by heating the regenerated air in the second section 320 is heating by utilizing waste heat, and
The heat amount Δi obtained by cooling the regeneration air at 0 is the dehumidification cooling effect, and the heat recovery by the heat exchanger as an economizer is Δ
H.

The second embodiment of the present invention will be described with reference to FIGS. The difference of this embodiment from the first embodiment shown in FIG. 1 is that the heat exchanger 300b is provided between the evaporation sections of the plane PB and the plane PC and between the evaporation sections of the plane PD and the plane PE. That is, apertures 331 and 332 are provided between them. That is, in the drawing, the end of the evaporation section 251B in the plane PB and the end of the evaporation section 251C in the plane PC are:
The end of the evaporating section 251D in the plane PD and the end of the evaporating section 251E in the plane PE are connected through the stop 332.

In such a configuration, the refrigerant C introduced into the evaporating section 251B is
Part of the evaporator B evaporates, becomes wet, is decompressed by the throttle 331, and flows into the evaporator section 251C in the plane PC. Here it evaporates further and the condensing section 252C
Flows into. The air is further turned by the U-tube and flows into the condensing section 252D, and is further condensed and flows into the evaporating section 251D. Here, a part of the refrigerant C evaporates and reaches the throttle 332. Here, the pressure is reduced to the evaporating section 251E in the plane PE, and then to the condensing section 2
Flow into 52E. The refrigerant C that has been sufficiently condensed here reaches the path 204 and the expansion valve 250, is decompressed, and flows into the evaporator 210.

Here, the evaporation sections 251A, 251
Evaporating pressure at B, and condensing section 252A, 2
The condensing pressure at 52B, ie, the first intermediate pressure, or the pressure at the evaporating sections 251C, 251D, the condensing sections 252C, 252D, ie, the second intermediate pressure, depends on the temperature of the regeneration air B before entering the evaporator 210, The temperature is determined by the temperature of the regenerated air B after entering the evaporator 210.

Since the heat exchanger 300 shown in FIG. 1 or the heat exchanger 300b shown in FIG. 5 utilizes the heat transfer of evaporation and the heat of condensation, it has a very high heat transfer coefficient, and The heat exchange efficiency is very high in the vessel 300b because the heat is exchanged in a counter-current manner. The refrigerant C is supplied to the evaporating section 251.
From the condensing section 252, also the condensing section 252
Since the air is forced to flow in substantially one direction as a whole in the refrigerant path, such as from the evaporating section 251, the heat exchange efficiency between the high-temperature regeneration air B and the low-temperature regeneration air B is high. Here, flowing in substantially one direction as a whole means that, for example, in the case of a turbulent flow, even if there is a reverse flow locally, a pressure wave is generated due to generation of bubbles or instantaneous interruption, and the refrigerant C flows in the flow direction. Even if it vibrates, it means that it flows almost in one direction in the refrigerant path as a whole. In this embodiment, the refrigerant C is forcibly flowed in one direction at a pressure increased by the compressor 260.

Here, the heat exchange efficiency φ means that the inlet temperature of the heat exchanger on the high temperature side is TP1, the outlet temperature is T, the inlet temperature of the heat exchanger on the low temperature side is TC1, and the outlet temperature is TC.
When focusing on the cooling of the fluid on the high-temperature side, that is, when the purpose of heat exchange is cooling, φ = (TP1-T
P2) / (TP1-TC1), when attention is paid to heating of a low-temperature fluid, that is, when the purpose of heat exchange is heating, φ =
It is defined as (TC2-TC1) / (TP1-TC1).

The operation of the heat pump HP2 according to the second embodiment shown in FIG. 5 will be described with reference to FIG. In the figure, points a to e are the same as those in the first embodiment of FIG. In addition, the refrigerant C in the state of the point e which flows into the evaporating section 251A of the heat exchanger 300b.
As described with reference to FIG. 3, a part of the liquid evaporates at the first intermediate pressure and the liquid and the gas are mixed.

The refrigerant C further evaporates in the evaporating section 251A, and reaches a point f1 in the Mollier diagram that approaches the saturated gas line in the wet area. In this state, the refrigerant C enters the condensing section 252A, where it is condensed and reversed in the U-tube to enter the condensing section 252B, where it is further condensed, reaching a point g1 in the wet area but close to the saturated liquid line. Here, it enters the evaporating section 251B, heads in the direction of the saturated gas line in the wet area, and reaches the point h1a. Up to this point, the change is almost at the first intermediate pressure.

The refrigerant C in the state of the point h1a is reduced in pressure through the throttle 331, and reaches the point h1b at the second intermediate pressure. That is, the refrigerant flows from the evaporating section 251B, which is the refrigerant path in the plane PB, to the evaporating section 251C, which is the refrigerant path of the plane PC, via the throttle 331. This refrigerant C
Further evaporates at the second intermediate pressure in the evaporating section 251C to reach the point f2. After that, similarly, the condensation and the evaporation are alternately repeated, and the pressure is reduced by the intermediate throttle 332.
The pressure becomes the third intermediate pressure and the evaporating section 251
E, the refrigerant C that has passed through the condensing section 252E and the refrigerant path, corresponds to a point g2 on the Mollier diagram corresponding to the point g2 in FIG.
It reaches three. This point is on the saturated liquid line in the Mollier diagram.
The temperature is 11 ° C. and the enthalpy is 215.0 kJ / kg.

As in the case of FIG. 3, the refrigerant liquid C at the point g3 is supplied to the throttle 250 at a saturation pressure of 0.30M at a temperature of 1 ° C.
The pressure is reduced to Pa, the state at the point j is reached, and the refrigerant liquid C at 1 ° C.
Reaches the evaporator 210 as a mixture of water and gas, where it removes heat from the regenerated air B, evaporates and becomes a saturated gas at the point a on the Mollier diagram, is sucked into the compressor 260 again, and repeat.

As described above, in the heat exchanger 300b, the refrigerant C alternately changes the state of evaporation / condensation, and has a very high heat transfer coefficient because of the evaporation heat and the condensation heat. The points are the same as those of the heat exchanger 300 of the first embodiment.

In the heat exchanger 300b, the evaporator 210
In the first section 310, the regenerated air B before being cooled in the evaporating section 251A, 251B, 251C,
Heat exchange is performed in the order of 51D and 251E. That is, the temperature gradient of the regeneration air B and the temperature gradient of the evaporating section 251 are in the same direction. Similarly, the regenerated air B cooled by the evaporator 210 exchanges heat in the second section 320 in the order of the condensation sections 252E, 252D, 252C, 252B, and 252A. That is, the temperature gradient of the regeneration air B and the temperature gradient of the condensation section 252 are in the same direction. From this, the regenerated air B before and after being cooled by the evaporator 210
It means that heat exchange is performed between the two in a counterflow relationship.
Therefore, in the heat exchanger 300b, an extremely high heat exchange efficiency can be achieved in combination with the use of the evaporation heat transfer and the condensation heat transfer.

The enthalpy difference available in the evaporator 210 is significantly larger than that of the conventional heat pump, and the amount of gas circulating through the compressor for the same cooling load and, consequently, the required power are reduced by 20% (1- (620) .1-472.2)
/(620.1-434.9)=0.20) is also the same as in FIG.

The operation of the dehumidifier provided with the heat pump HP2 is qualitatively the same as that described with reference to the psychrometric chart of FIG.

Next, FIG. 7 shows a flowchart of the dehumidifying device 23 according to the third embodiment. Heat exchanger 300 used in the first embodiment, heat exchanger 30 used in the second embodiment
In the heat exchanger 300c corresponding to 0b, the throttles 331, 3
32 is provided on the condensation section 252 side. Other configurations are the same as those of the second embodiment described with reference to FIG.

FIG. 8 is a Mollier diagram of the heat pump HP3 shown in FIG. Unlike the case of FIG. 6, the pressure is reduced during the condensation process at the intermediate pressure. That is, the aperture 3
At 31, the pressure is reduced from the point g 1 a to the point g 1 b, and at the throttle 332, the pressure is reduced from the point g 2 a to the point g 2 b. The point that the heat exchange between the regenerated air B before and after being cooled by the evaporator 210 is a counterflow is the same as the embodiment of FIG.

In each of the drawings, a drain pan 451 is shown, but this is not limited to the evaporator 210, and the heat exchanger 30
It is preferable to provide so as to cover below 0, 300b and 300c. In particular, it is preferable to provide it below the first section 310. This is because in the first section 310 of the heat exchangers 300, 300b, and 300c, the regeneration air B is precooled, but some moisture may condense here.

Referring to FIG. 9, heat exchanger 300 of the present invention
An example of the structure of d will be further described. (A) is a plan view seen in the flow direction of the low-temperature regeneration air B and the high-temperature regeneration air B, and (b) is a side view seen from the direction perpendicular to the flow of the low-temperature and high-temperature regeneration air. That is, (a) is a view on arrow AA of (b). In (a), the regenerated air B having a low temperature flows from the near side of the paper to the front, and the regenerated air B having a high temperature flows from the front to the near side. In this heat exchanger 300d, the tubes are provided with low-temperature and high-temperature regenerated air B
Are arranged in eight rows in each of four planes PA, PB, PC, PD orthogonal to the flow. That is, they are arranged in four rows and eight columns along the flow of the regeneration air B. Plane P
A plane PE (not shown) may be provided below D, and eight more rows may be arranged in the plane PE. 1, 5, and 7, for convenience, the heat exchange tubes in each of the planes PA, PB, PC, and PD have been described as being in one row and one column. Tube rows are included.

An intermediate stop 331 is provided at a position where the first plane PA moves to the next plane PB, a middle stop 332 (not shown) is provided at a position where the plane PB is moved to the plane PC, and a middle position of the intermediate stop 332 is formed at a position where the plane PC moves to the plane PD. An intermediate stop 333 is provided.
Here, one stop is provided at a position where one plane moves to the next plane. However, for example, a tube row belonging to PA may be formed of a plurality of layers. An intermediate stop is provided at a position where each layer moves to the next layer. In this case, the planes before and after the intermediate stop are referred to as a first plane and a second plane.

Further, heat exchangers having eight rows and four layers (rows) as shown in FIG. 9 may be arranged in parallel with the flow of the processing air at low and high temperatures in accordance with the flow rates thereof. , May be arranged in series.

Further, for example, in the Mollier diagram of FIG. 8, the repetition of the evaporation and condensation of the refrigerant C is established as a cycle even if the refrigerant C enters the supercooling region beyond the saturated liquid line, but is formed by heat exchange between the regenerated air. Considering this, the phase change of the refrigerant C is preferably performed in the wet region.
Therefore, in the heat exchanger 330d shown in FIG.
Preferably, the heat transfer area of the first evaporator section connected to zero is greater than the heat transfer area of the subsequent evaporator section. Also, since the refrigerant C flowing into the throttle 250 is preferably in a saturated or supercooled region, the heat transfer area of the condensing section connected to the throttle 250 is configured to be larger than the heat transfer area of the previous condensing section. Is preferred.

The heat exchanger is inexpensive and is economical when used instead of an expensive heat pipe. Unlike the heat pipe, the working fluid can be made the same as that of the heat pump, so that maintenance is not required.

In the embodiment described above, the regeneration air B
An evaporator 210 for cooling the air below the dew point, a first section 310 of the heat exchangers 300, 300b, 300c for pre-cooling the regeneration air B, a condenser 220 for heating the regeneration air B,
Heat exchangers 300, 300b, and 3 for preheating regeneration air B
Since the same refrigerant C is used for the second section 320 of the second evaporator 00c, the refrigerant system is simply simplified, and the evaporator 2
10. Since the pressure difference between the condensers 220 can be utilized, the circulation becomes active, and the boiling phenomenon accompanying the phase change can be applied to the heat exchange of pre-cooling and pre-heating, so that the efficiency can be increased. .

In the above embodiment, the dehumidifying device for dehumidifying an air-conditioned space has been described. However, the present invention is not necessarily limited to the air-conditioned space, and the dehumidifying device of the present invention can be applied to other spaces requiring dehumidification. .

[0100]

As described above, according to the present invention, there is provided a moisture adsorber for adsorbing the moisture of the processing air and regenerating with the regenerated air, and a condenser for heating the regenerated air upstream of the moisture adsorber. An evaporator that cools the regenerated air to a temperature below the dew point on the downstream side of the moisture adsorption device, a booster that pressurizes the refrigerant evaporated by the evaporator and sends it to the condenser, and flows between the moisture adsorption device and the evaporator. A heat pump having a heat exchanger for exchanging heat between regeneration air and regeneration air flowing between the evaporator and the condenser is provided, and the regeneration air is configured to be circulated. Therefore, the regeneration air can be pre-cooled by the heat exchange means before cooling in the evaporator, and the cold heat of the pre-cooling can be recovered from the regeneration air once cooled in the evaporator,
A dehumidifier provided with a heat pump having a high operation coefficient can be provided, and a dehumidifier having a high dehumidification capacity per energy consumption can be provided.

The treated air is not cooled by an evaporator to remove water, but is removed by a moisture adsorption device. Therefore, the dew point temperature is lower than freezing point, that is, 4 g.
It is also possible to obtain air having a low absolute humidity of not more than / kgDA.

[Brief description of the drawings]

FIG. 1 is a flowchart of a dehumidifying apparatus according to a first embodiment of the present invention.

FIG. 2 is a schematic front sectional view showing the structure of the dehumidifier shown in FIG.

FIG. 3 is a Mollier diagram of a heat pump of the dehumidifier shown in FIG.

FIG. 4 is a psychrometric chart for explaining the operation of the dehumidifier of FIG. 1;

FIG. 5 is a flowchart of a dehumidifier according to a second embodiment of the present invention.

FIG. 6 is a Mollier diagram of a heat pump of the dehumidifier shown in FIG.

FIG. 7 is a flowchart of a dehumidifier according to a third embodiment of the present invention.

8 is a Mollier diagram of the heat pump of the dehumidifier shown in FIG.

FIG. 9 is a schematic plan sectional view and a sectional side view of a heat exchanger suitable for use in a heat pump of a dehumidifier according to an embodiment of the present invention.

FIG. 10 is a flowchart of a conventional dehumidifying air conditioner.

[Explanation of symbols]

21, 22, 23 Dehumidifier 101 Air-conditioned space 102, 140 Blower 210 Evaporator 220 Condenser 251, 251A, 251B, 251C, 251D, 2
51E evaporation section 252, 252A, 252B, 252C, 252D, 2
52E Condensing section 250 Restrictor 260 Compressor 300, 300b, 300c, 300d Heat exchanger 310 First section 320 Second section 330 Restrictor 331, 332 Intermediate restriction HP1, HP2, HP3 Heat pump PA, PB, PC, PD, PE Plane

 ──────────────────────────────────────────────────続 き Continued on the front page F term (reference) 3L053 BC01 BC09 4D052 AA08 BA04 BB02 BB04 BB09 CB00 DA02 DA08 DB01 GA03 GA04 GB02 GB03 GB04 HA01 HA03 HB02

Claims (4)

[Claims] 1. A moisture adsorbing device that adsorbs moisture of treated air and desorbs moisture by regenerating air to regenerate the water; and condensing refrigerant to heat the regenerated air upstream of the moisture adsorbing device. An evaporator that cools the regenerated air to a temperature below the dew point downstream of the moisture adsorption device by evaporating the refrigerant, and a booster that boosts the refrigerant evaporated by the evaporator and sends it to the condenser. And a heat pump having a heat exchanger that exchanges heat between the regeneration air flowing between the moisture adsorption device and the evaporator, and the regeneration air flowing between the evaporator and the condenser. Preparation;
The regeneration air is configured to be circulated; a dehumidifier. 2. The heat exchanger includes a group of small tubes connecting the condenser and the evaporator; the group of small tubes is configured to guide the refrigerant condensed in the condenser to the evaporator. The regeneration air flowing between the moisture adsorption device and the evaporator, and the regeneration air flowing between the evaporator and the condenser are alternately contacted with each other. The dehumidifier according to claim 1. 3. The heat exchanger includes a first section through which the regeneration air flows between the moisture adsorption device and the evaporator, and a section through which the regeneration air flows between the evaporator and the condenser. Second
And the capillary tube group is connected to the condenser via a first throttle, and after passing through the first and second sections alternately and repeatedly, the second throttle is closed. The dehumidifier according to claim 2, wherein the dehumidifier is configured to be connected to the evaporator through an evaporator. 4. The first section and the second section,
The regenerated air flowing through each of the compartments is configured to flow in opposition to each other; the group of thin tubes in the first compartment and the second compartment are arranged on a first surface substantially orthogonal to the flow of the regenerated air. Having at least one pair of first and second partition penetrations, and at least one pair in a second plane that is substantially orthogonal to the flow of the regeneration air that is different from the first plane. 4. The dehumidifier according to claim 3, further comprising a first partition penetrating portion and a second partition penetrating portion, and having an intermediate restrictor at a position moving from the first plane to the second plane. 5. .