JP2001074275A - Dehumidifying device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a dehumidifying air conditioner, high in COP and compact in structure. SOLUTION: A dehumidifying device is provided with a moisture adsorbing device 103, having a desiccant for adsorbing moisture in treating air A, and a heat pump HP1, having a booster 260 for boosting refrigerant and pumping up heat by boosting the refrigerant by the booster employing the treating air A as a low temperature heat source and reproducing air B for reproducing the desiccant as a high temperature heat source. Heat exchange is effected between the reproducing air B before being heated by pumping the heat up, and treating air A after adsorbing moisture by the moisture adsorbing device before being cooled by pumping the heat up, whereby the heat exchange is effected by circulating the liquid between the reproducing air side and the treating air side. The heat pump HP1 supercools the refrigerant, condensed by pumping heat up, by outdoor air, introduced as the reproducing air B. Heat exchange between the reproducing air and the treating air is effected by circulating the liquid between both of them whereby the compact dehumidifying device or, especially, a dehumidifying air conditioner can be provided while the refrigerant is supercooled whereby the COP of the heat pump can be improved.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

[0001] The present invention relates to a dehumidifying air conditioner, and more particularly to a dehumidifying air conditioner using a desiccant.

[0002]

2. Description of the Related Art As shown in FIG. 5, there has conventionally been an air conditioning system in which a heat pump as a heat source is combined with a so-called desiccant air conditioner. In this air conditioning system, a compression heat pump HP using a compressor 260 is used as a heat pump. This air-conditioning system includes a path of the processing air A in which moisture is adsorbed by the desiccant rotor 103,
After being heated by a heating source, the desiccant rotor 103 having the moisture adsorbed therein passes through the desiccant rotor 103 and has a path for regenerating air B for desorbing and regenerating moisture in the desiccant. An air conditioner having a sensible heat exchanger 104 between the desiccant (desiccant) and the regeneration air before being heated by the heating source;
Having a compression heat pump HP, and using the high heat source of the compression heat pump HP as a heating source to heat the regeneration air of the air conditioner with the heater 220 to regenerate the desiccant, and use the low heat source of the compression heat pump HP as a cooling heat source. The cooler 210 cools the processing air of the air conditioner.

In this air conditioning system, the compression heat pump HP is configured to simultaneously cool the processing air of the desiccant air conditioner and heat the regeneration air, so that the compression heat pump HP is driven by driving energy externally applied to the compression heat pump HP. Generates the cooling effect of the processing air, and furthermore, the desiccant can be regenerated by the heat obtained by adding the heat pumped from the processing air by the heat pump action and the driving energy of the compression heat pump HP. High energy saving effect can be obtained.

Here, referring to the Mollier diagram of FIG. 6, FIG.
The operation of the compression heat pump HP shown in FIG. FIG. 6 is a Mollier diagram of the refrigerant HFC134a.
Point a indicates the state of the refrigerant evaporated in the cooler 210, and is in the state of a saturated gas. The pressure is 4.2 kg / cm ² , the temperature is 10 ° C., and the enthalpy is 148.83 kcal / kg. The state where the gas is sucked and compressed by the compressor 260 and the state at the discharge port of the compressor 260 are indicated by a point b. In this state, the pressure is 19.3 kg / cm ² , the temperature is 78 ° C., and the state is a superheated gas. This refrigerant gas is cooled in the heater (cooler or condenser as viewed from the refrigerant side) 220 and reaches a point c on the Mollier diagram. This point is a saturated gas state, the pressure is 19.3 kg / cm ² , and the temperature is 65 ° C. Under this pressure, it is further cooled and condensed,
The point d is reached. This point is in the state of a saturated liquid, the pressure and temperature are the same as in point c, the pressure is 19.3 kg / cm ² , the temperature is 65 ° C., and the enthalpy is 122.97 kcal / k.
g. This refrigerant liquid is depressurized by the expansion valve 270 and depressurized to a saturation pressure of 4.2 kg / cm ² at a temperature of 10 ° C., and as a mixture of the refrigerant liquid and gas at 10 ° C., a cooler (evaporator as viewed from the refrigerant) At 210, heat is removed from the processing air and evaporated to become a saturated gas in the state of the point a on the Mollier diagram, sucked into the compressor 260 again, and the above cycle is repeated.

[0005] In FIG. 5, the processing air (state K) from the air-conditioned space 101 is desiccant adsorbed by the desiccant rotor 103 to lower the absolute humidity.
The dry bulb temperature is raised by the heat of adsorption of the desiccant to reach the state L, and further cooled by the sensible heat exchanger 104 with the absolute humidity kept constant to become air in the state M, and enters the cooler 210. Here, the air is further cooled at a constant absolute humidity to become air in state N, and returned to the air-conditioned space 101. On the other hand, the outside air in the state Q is sent to the sensible heat exchanger 104 by the blower 140, where the air itself is heated by cooling the processing air to the state R, and then heated by the heater 220 to the state T. Become
By regenerating the desiccant by the desiccant rotor 103, the absolute humidity is high, the dry-bulb temperature is lowered, and the state U is reduced.
And is exhausted EX.

In such a system, a rotary heat exchanger or a cross-flow heat exchanger has been used as the sensible heat exchanger.

[0007]

According to the conventional air conditioning system described above, the sensible heat exchanger 104, which preliminarily cools the processing air before cooling it with the cooler 210, plays an important role. However, rotary heat exchangers are expensive and cross-flow heat exchangers have not always demonstrated satisfactory performance. Further, since the sensible heat exchanger 104 generally occupies a large volume in the system, the system configuration becomes difficult, and the system must be increased in size.

Therefore, an object of the present invention is to provide a compact and dehumidifying air conditioner having a high COP.

[0009]

In order to achieve the above object, a dehumidifier according to the first aspect of the present invention is, for example, shown in FIG.
As shown in FIG. 3, a moisture adsorbing device 103 having a desiccant for adsorbing moisture in the processing air A; and a booster 260 for increasing the pressure of the refrigerant, and a regeneration air for regenerating the desiccant using the processing air A as a low heat source. B as a high heat source, booster 2
A heat pump HP1 for pumping heat by increasing the pressure of the refrigerant at 60; regenerated air B before being heated by pumping the heat;
Is configured to exchange heat with the processing air A after moisture has been adsorbed in the processing air A and before being cooled by being pumped up by the heat; Circulating between the regeneration air side and the processing air side;
P1 is due to the outside air taken in as regeneration air B,
The refrigerant condensed by pumping the heat is supercooled. The booster is typically a compressor that compresses a refrigerant gas. The liquid is preferably water having a large specific heat. The outside air taken in as the regeneration air B, which supercools the refrigerant condensed by pumping the heat, is typically outside air that has not been subjected to any heat exchange in the dehumidifier. That is, it is preferable to use outside air before heat exchange with the processing air A as regeneration air.

[0010] With this configuration, the heat exchange between the regeneration air and the processing air is performed by circulating the liquid between the two. It can be provided and is configured to supercool the refrigerant, thereby improving the COP of the heat pump.

A dehumidifier according to a second aspect of the present invention includes, as shown in FIG. 1, a moisture adsorber 103 having a desiccant for adsorbing moisture in the processing air A;
A booster 260 for increasing the pressure of the refrigerant; a first heat installed in a regeneration air path to the moisture adsorption device 103 for heating the regeneration air B for regenerating the desiccant with the heat of condensation of the refrigerant which has been increased in pressure by the compressor 260. Exchanger 220; water adsorption device 10
A second heat exchanger 320 installed in the regeneration air path to the upstream side of the flow of the regeneration air from the first heat exchanger 220 in the regeneration air path to heat the regeneration air with the sensible heat of the liquid; A third heat exchanger 310 installed in the processing air path from the device 103; and a processing air path from the moisture adsorber 103 installed downstream of the flow of the processing air A from the third heat exchanger 310. A fourth heat exchanger 210 provided;
The fourth heat exchanger 210 is configured to cool the process air with the sensible heat of the liquid; the fourth heat exchanger 210 cools the process air with the evaporation heat of the refrigerant pressurized by the pressurizer 260. A fifth heat exchanger 225 disposed in a refrigerant path for guiding the refrigerant condensed in the first heat exchanger 220 to the fourth heat exchanger 210; a second heat exchanger 3
20 is configured to circulate the liquid between the third heat exchanger 310; the fifth heat exchanger 225 comprises:
The refrigerant condensed in the first heat exchanger 220 is supercooled. As the liquid to be circulated, typically, water having a large specific heat is preferable.

Here, the first heat exchanger and the second heat exchanger may be integrally formed, and similarly, the third heat exchanger and the fourth heat exchanger may be integrated.
Heat exchangers may be integrally configured. Further, it is particularly preferable that the second heat exchanger and the third heat exchanger are configured so that the flow of the liquid is opposite to the flow of the regeneration air or the flow of the processing air. Since the heat exchange uses the sensible heat of the liquid, the heat exchange efficiency can be increased by using the counter flow.

[0013] In addition, as described in claim 3, claim 2
, The second heat exchanger 320 and the fifth heat exchanger 225 may be arranged in parallel in the flow of the regeneration air.

Here, it is preferable that the second heat exchanger and the fifth heat exchanger are integrally formed. In addition, the first, second, fifth
Of the heat exchanger may be integrated. With this configuration, since the fifth heat exchanger is provided, the refrigerant can be further cooled.

[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 flowchart of an air conditioning system having a dehumidifying air conditioner, that is, a desiccant air conditioner according to an embodiment of the present invention. FIG. 2 is a psychrometric chart of the dehumidifying air conditioner of FIG. A refrigerant Mollier diagram of the heat pump HP1 included in the air conditioning system of FIG. 1, and FIG. 4 is a diagram illustrating an example of a mechanical arrangement of the dehumidifying air conditioner of FIG.

Referring to FIG. 1, the structure of a dehumidifying air conditioner according to an embodiment of the present invention will be described. In this air conditioning system, the humidity of the processing air is reduced by a desiccant (drying agent), and the air-conditioned space 101 to which the processing air is supplied is maintained in a comfortable environment. In the figure, along the path of the processing air A from the air-conditioned space 101, a path 107, a blower 102 for circulating the processing air, a path 108, a desiccant rotor 103 as a moisture adsorber filled with desiccant, a path 109, and processing air A third heat exchanger 310 for cooling
Path 110, refrigerant evaporator (cooler as viewed from processing air) 21 as fourth heat exchanger for further cooling processing air
0, the path 111, and the like, and are configured to return to the air-conditioned space 101.

Along the path from the outdoor OA to the regeneration air B, first, the outside air passes through a path 124, a blower 140 for circulating the regeneration air, a path 125, a path 125A and a path 125B branched in parallel from the path 125, and a path. A second heat exchanger located along 125A, path 126A, and a fifth heat exchanger located along path 125B, path 1
26B, and a path 126 that collects the paths 126A and 126B, a refrigerant condenser (heater as viewed from regenerated air) 220 as a first heat exchanger, a path 127, a desiccant rotor 103, and a path 128, in this order. And is configured to exhaust EX to the outside.

Here, the heat medium that exchanges heat with the regeneration air in the second heat exchanger 320 and the heat medium that exchanges heat with the processing air in the third heat exchanger 310 are a common heat medium. The heat medium circulation pump 330 is configured to circulate between the two heat exchangers. That is, the heat medium outlet of the second heat exchanger 320 and the suction port of the circulation pump 330
3, the outlet of the circulation pump 330 and the heat medium inlet of the third heat exchanger 310 are connected by a path 301, and the heat medium outlet of the third heat exchanger and the second heat exchanger 320 Are connected by a path 302. An expansion tank 34 for compensating for thermal expansion or contraction of the heat medium or leakage of the heat medium is provided in the path 303.
0 is provided. As heat medium, specific heat is large,
That is, it is preferable to use inexpensive water, which has a large heat capacity per unit weight, does not pollute the environment if leaked, and is inexpensive.

The second heat exchanger 320 and the third heat exchanger 3
10 preferably has a plate fin structure. That is, a plurality of heat exchange tubes are arranged side by side, and each tube is configured to penetrate the plate fin. U (tube) tubes are attached to the ends of these tubes, and the adjacent tubes communicate with each other so that the heat exchange tubes have a multi-pass structure as a whole. Water as a heat medium flows through the tube, and processing air or regeneration air that exchanges heat with water flows outside the tube, that is, on the plate fin side. The order of flow of water in each of the tubes arranged in a plurality of passes is such that the flows of water and air are countercurrent.

That is, as shown in FIG. 1, in the third heat exchanger 310, the water discharged by the pump 330 first tries to flow out of the third heat exchanger, and the temperature has already become low. It comes into contact with the processing air, gradually flows into the processing air at a higher temperature, and finally flows into contact with the processing air on the inflow side. And as the heated water, the third heat exchanger 3
Outflow 10 Similarly, the water that has flowed out of the third heat exchanger 310 first comes into contact with the high-temperature regeneration air that is going to flow out of the second heat exchanger 320, and gradually comes into contact with the low-temperature regeneration air. Finally, it flows so as to come into contact with the regeneration air on the inflow side. Then, it flows out of the second heat exchanger 320 as water whose temperature has decreased.

As described above, the water and the air as the heat medium are
Since heat is exchanged in the counterflow, high heat exchange efficiency can be obtained.
Consequently, the third heat exchanger 310 and the second heat exchanger 32
Process air A and regeneration air (outside air) that exchange heat via
Paying attention to the flow of B, heat exchange is performed between the two in the opposite flow, so that high heat exchange efficiency can be realized.

The second heat exchanger 320 and the fifth heat exchanger 2
25 is integrally formed. That is, a plurality of plate fins arranged in parallel and at equal intervals include a plurality of heat exchange tubes arranged in parallel and at equal intervals so as to penetrate perpendicularly to the plate fins.
Of the plurality of heat exchange tubes, the portion constituting the second heat exchanger and the portion constituting the fifth heat exchanger are divided into groups, and the tubes of each group are connected by U tubes. .

Further, along a path of the refrigerant from the refrigerant evaporator 210, a path 205, a compressor 260 for compressing the refrigerant evaporated and gasified by the refrigerant evaporator 210, a path 201,
Refrigerant condenser 220, path 202, fifth heat exchanger 22
5, the path 203, the expansion valve 250, and the path 204 are arranged in this order, and are configured to return to the fourth heat exchanger 210. Thus, the refrigerant evaporator 210, the compressor 2
The heat pump HP1 includes the refrigerant pump 60, the refrigerant condenser 220, the fifth heat exchanger 225, and the expansion valve 250.

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 with a gap through which gas can pass. For example, a large number of tubular drying elements are bundled so that the central axis thereof is parallel to the rotation axis AX. The desiccant rotor 103 rotates in one direction around the rotation axis AX, and the processing air A and the regeneration air B flow in and out in parallel with the rotation axis AX. Each drying element is
As the rotor 103 rotates, it is arranged so as to alternately contact the processing air A and the regeneration air B.

Generally, the processing air A and the regeneration air B are respectively parallel to the rotation axis AX, and each of the circular desiccant rotors 10
3 is formed so as to flow in the thickness direction of the rotor 103 in a counterflow manner in substantially half the area. The flow paths of the processing air and the regeneration air are separated by a suitable partition plate (not shown) so that the air of both systems does not mix with each other.

The operation of the embodiment of the present invention will be described with reference to FIG. 2 and the configuration as appropriate with reference to FIG. In FIG. 2, the alphabetic symbols K to N and Q to U indicate the state of air in each part. This symbol is shown in FIG.
In the flowchart in FIG.

First, the flow of the processing air A will be described. 2, the processing air (state K) from the air-conditioned space 101 is:
The air is sucked by the blower 102 through the processing air path 107 and is sent to the desiccant rotor 103 through the processing air path 108. Here, the moisture is adsorbed by the desiccant in the drying element to lower the absolute humidity, and the dry bulb temperature is raised by the heat of adsorption of the desiccant to change the state L.
To reach. This air is sent through process air path 109 to a third heat exchanger 310 where the absolute humidity remains constant.
It is cooled by the water flowing in the tube to become air in the state M, and enters the cooler 210 through the path 110. The refrigerant that evaporates here is further cooled at a constant absolute humidity to become air in state N. This air is dried and cooled, and is returned to the air-conditioned space 101 via the duct 111 as the processing air SA having an appropriate humidity and an appropriate temperature.

Next, the flow of the regeneration air B will be described. In FIG. 2, the regeneration air (state Q) from the outdoor OA is sucked in by the blower 140 through the regeneration air path 124 and sent to the second heat exchanger 320 through the path 125 and the path 125A. Here, heat exchange is performed with the water flowing in the tube to raise the dry bulb temperature to become air in state R.

The air sucked in and discharged by the blower 140 passes through the path 125 and a path 125B arranged in parallel with the path 125A to pass through the fifth heat exchanger 22.
It is sent to 5. Here, after being heated by the refrigerant flowing in the tube, it joins the path 126 through the path 126B. However, depending on the structure of the second heat exchanger 230 and the fifth heat exchanger 225, the path 126B may be configured to exhaust the air passing therethrough.

The air that has joined the path 126 is sent to a refrigerant condenser (heater as viewed from the regeneration air) 220, where it is heated to increase the dry bulb temperature to become air in state T. This air is sent to the desiccant rotor 103 through the path 127, where it takes water from the desiccant in the drying element and regenerates it, thereby increasing the absolute humidity and lowering the dry bulb temperature by the desiccant moisture desorption heat. To reach the state U. This air is exhausted EX through a path 128 and a path 129.

The blower 140 is connected to the route 124 and the route 1
The distance may be any location as long as it is a path of the regeneration air. For example, it may be inserted and arranged in the path 128 (see FIG. 4 described later). Blower 10 for process air
Similarly, the second device may be installed anywhere as long as it is a processing air path.

In the air conditioner described above, the amount of heat added to the regeneration air for regeneration of the desiccant of the device is represented by ΔH, as can be seen from the cycle on the air side shown in the psychrometric chart of FIG. Assuming that the amount of heat pumped from the air is Δq and the driving energy of the compressor is Δh, ΔH = Δq + Δh. Cooling effect Δ obtained as a result of regeneration with this heat quantity ΔH
Q increases as the temperature of the external air (state Q) for heat exchange with the treated air after adsorption of moisture (state L) decreases. Also, the larger the temperature difference between the state Q and the state M and the temperature difference between the state R and the state L, the larger the difference.

Next, referring to FIG. 3, heat pump HP1
The operation of will be described. FIG. 3 is a Mollier diagram when the refrigerant HFC134a is used. In this diagram, the horizontal axis is enthalpy and the vertical axis is pressure. In the figure, point a is the state of the refrigerant outlet of the cooler 210 shown in FIG. 1 and is the state of the saturated gas. The pressure is 4.2 kg / cm ² , the temperature is 10 ° C., and the enthalpy is 148.83 kcal / kg. The state where the gas is sucked and compressed by the compressor 260 and the state at the discharge port of the compressor 260 are indicated by a point b. In this state, the pressure is 19.3 kg / cm ² and the temperature is 78 ° C.

The refrigerant gas is supplied to a heater (refrigerant condenser) 2
It is cooled in 20 and reaches point c on the Mollier diagram. This point is a state of a saturated gas, and the pressure is 19.3 kg / c.
m ² , the temperature is 65 ° C. Under this pressure, it is further cooled and condensed to reach point d. This point is a state of a saturated liquid, the pressure and the temperature are the same as the point c, and the enthalpy is 12
2.97 kcal / kg.

This refrigerant liquid heats the regenerated air in the fifth heat exchanger 225 and deprives itself of heat and is supercooled. However, it may be supercooled to some extent in the heater 220, and the fifth heat exchanger 225 may be configured to increase the degree of subcooling. In the heater 220, most of the refrigerant is condensed. The refrigerant may flow into the fifth heat exchanger 220 as a gas to condense the gas and supercool the condensed liquid.

The refrigerant liquid supercooled in the fifth heat exchanger 225 reaches point e. This point means that the pressure is at point c or d.
The temperature is about 30 ° C. and the enthalpy is 109.
It is 99 kcal / kg.

The refrigerant liquid in the state at the point e is reduced in pressure by the expansion valve 250 and reaches the point j. At this point, the pressure is 4.2 kg / cm ² , the temperature is 10 ° C., and the enthalpy is
It is 109.99 kcal / kg similarly to the above.

As described above, according to this embodiment, the second heat exchanger 32 is compact and has high heat exchange efficiency.
0 and the third heat exchanger 310 can maintain a high COP, and the heat pump HP1 includes the fifth heat exchanger. The COP can be significantly improved as compared with the case where the refrigerant in the state of the point d in the device 220 is returned to the cooler (evaporator) 210 via the throttle.

That is, the difference in enthalpy usable in the cooler (evaporator) 210 is 25.5 in the conventional heat pump HP.
In contrast to 86 kcal / kg, the heat pump HP1 according to the present embodiment has a capacity of 148.83-109.9.
9 = 38.84 kcal / kg, and the amount of gas circulating through the compressor for the same cooling load, and consequently the required power, can be reduced by 33%. Conversely, in terms of the cooling effect that can be achieved with the same power, the cooling effect can be increased by 50%. That is, as a result of using the subcool cycle, a remarkably high COP can be achieved.

Referring to FIG. 4, an example of the mechanical arrangement of the dehumidifying air conditioner described above will be described. In FIG. 4, devices constituting the apparatus are housed in a cabinet 700. Cabinet 700 is formed as a rectangular parallelepiped housing made of, for example, a thin steel plate, and has a processing air RA suction port opened at the center of the uppermost ceiling portion.
A filter 501 is provided at the opening to prevent dust from the air-conditioned space from being brought into the device. Filter 5
01 inside the cabinet 700.
Is installed, and its suction port communicates with the processing air suction port of the cabinet via the filter 501.

Below the blower 102 in the vertical direction, a semicircular region of the desiccant rotor 103 on the processing air side is arranged. The desiccant rotor 103 is configured to be rotationally driven by a chain by an electric motor 105 having a rotation axis substantially parallel to the rotation axis AX.

A third heat exchanger 310 is provided vertically below the processing air side region of the desiccant rotor 103 via a path 109, and further below the fourth heat exchanger (a refrigerant evaporator). ) 210 are arranged. The heat exchanger 310 and the heat exchanger 210 are integrally formed. That is, it is configured to include a plurality of heat exchange tubes that penetrate perpendicularly to the common plate fin.

A path 111 is provided below the fourth heat exchanger 210 in the vertical direction. The path 111 is drawn horizontally in the horizontal direction, the direction of the path 111 is changed to the upper side in the vertical direction, and the processing is performed from the lower part in the vertical direction to the upper part. An air flow path is formed. The flow path is the processing air RA at the ceiling of the cabinet 700.
Side, and open to the outside through the ceiling portion, and supply air SA to air-conditioned space 101 (not shown in FIG. 4).
Is configured to be sent.

A pump 3 is provided in the horizontal pulling portion of the path 111.
An expansion tank 340 is provided at a portion of the path 111 that extends upward from below in the vertical direction.

On the other hand, a suction port for introducing outside air as regeneration air is provided below the side surface of the cabinet 700, and a filter 502 is provided at the suction port. The inside of the inlet forms a path 124,
A compressor 260 is provided in the path 124. The path 124 immediately turns vertically upward in the cabinet portion inside the filter 502. In this path, a second heat exchanger 320 and a fifth heat exchanger 225 are provided side by side with the third heat exchanger 310 in the horizontal direction. Above them vertically, a first heat exchanger (refrigerant condenser) 220 is provided. Heat exchanger 32
0, the heat exchanger 225, and the heat exchanger 220 are integrally formed. That is, it is configured to include a plurality of heat exchange tubes that penetrate perpendicularly to the common plate fin. Second heat exchanger 320 and third heat exchanger 310
As a heat medium circulating through the water flows through a water pipe connecting the two heat exchangers. That is, since both heat exchangers are connected by a water pipe, the degree of freedom of arrangement is higher than that of a rotary heat exchanger.

Above the first heat exchanger 220 in the vertical direction, a semicircular region of the desiccant rotor 103 on the regeneration air side is disposed. A space as a path 128 is formed vertically above a semicircular region on the regenerated air side of the desiccant rotor 103, and a blower 140 is installed therein. The outlet of the blower 140 is open at the ceiling of the cabinet 700 to the outside through the ceiling, along with the inlet of the processing air RA. As described above, the processing air having a relatively low temperature flows downward from above in the vertical direction, and the regeneration air having a relatively high temperature flows upward from below in the vertical direction, so that the flow is smooth. Further, since the rotation axis AX of the desiccant rotor is arranged in the vertical direction and the main devices are arranged in the vertical direction, the installation area of the apparatus can be reduced.

In the above embodiment, a compressor for compressing the refrigerant gas is used as the booster. However, it is sufficient that the refrigerant gas can be pressurized. For example, as in an absorption refrigerator, the refrigerant gas is absorbed by the absorbing liquid. It may be a combination of an absorber, a pump for pressurizing the absorbing liquid having absorbed the refrigerant gas, and a generator for generating the refrigerant gas from the pressurized and sent absorbing liquid.

[0049]

As described above, according to the present invention, since the heat exchange between the regeneration air and the processing air is performed by circulating the liquid between the two, the dehumidification unitized in a compact manner. An apparatus, in particular a dehumidifying air conditioner, can be provided.

When a fifth heat exchanger is provided in addition to the second heat exchanger and the third heat exchanger, the refrigerant liquid is supercooled, so that it is compact and has a high COP. It is possible to provide a dehumidifying device.

[Brief description of the drawings]

FIG. 1 is a flowchart of a dehumidifying air conditioner according to an embodiment of the present invention.

FIG. 2 is a psychrometric chart for explaining the operation of the dehumidifying air conditioner of FIG.

FIG. 3 is a Mollier diagram of a heat pump used in the dehumidifying air conditioner of FIG.

FIG. 4 is a front sectional view showing an example of a mechanical structure of the dehumidifying air conditioner according to the embodiment of the present invention.

FIG. 5 is a flowchart of a conventional dehumidifying air conditioner.

FIG. 6 is a Mollier diagram of a heat pump used in the conventional dehumidifying air conditioner shown in FIG.

[Explanation of symbols]

 101 air conditioning space 102, 140 blower 103 desiccant rotor 210 fourth heat exchanger (refrigerant evaporator) 220 first heat exchanger (refrigerant condenser) 225 fifth heat exchanger 250 expansion valve 260 compressor 310 third Heat exchanger 320 second heat exchanger 330 pump 340 expansion tank 501, 502 filter 700 cabinet HP1 heat pump

Continued on the front page F term (reference) 3L053 BC02 BC03 BC09 4D052 AA08 BA03 BA04 CB02 DA01 DA08 DB01 FA01 FA04 FA06 GA01 GA03 GB00 GB02 GB03 GB04 HA01 HA03 HB02 HB06

Claims (3)

[Claims] 1. A moisture adsorbing device having a desiccant for adsorbing moisture in process air; and a booster for pressurizing a refrigerant, wherein the process air is used as a low heat source, and the regeneration air for regenerating the desiccant is used as a high heat source. A heat pump that pumps heat by increasing the pressure of the refrigerant with the booster; regeneration air before being heated by being pumped by the heat, and treated air after moisture is adsorbed by the moisture adsorption device. And configured to exchange heat with the process air before being cooled by pumping the heat; wherein the heat exchange transfers liquid between the regeneration air side and the process air side. The heat pump supercools the refrigerant condensed by pumping the heat by the outside air taken in as the regeneration air. A dehumidifier. 2. A moisture adsorbing device having a desiccant for adsorbing moisture in the processing air; a booster for increasing the pressure of the refrigerant; and a regeneration air installed in a regeneration air path to the moisture adsorption device for regenerating the desiccant. A first heat exchanger that heats with the heat of condensation of the refrigerant pressurized by the pressure booster; a regeneration air path to the moisture adsorption device upstream of the flow of the regeneration air from the first heat exchanger; A second heat exchanger installed in the apparatus and heating the regenerated air with the sensible heat of the liquid; and a third heat exchanger installed in the processing air path from the moisture adsorption device;
In the processing air path from the moisture adsorption device, a fourth heat exchanger installed downstream of the third heat exchanger in the flow of the processing air.
The third heat exchanger is configured to cool the process air with sensible heat of a liquid;
Is configured to cool the processing air by the heat of evaporation of the refrigerant pressurized by the pressure booster; the refrigerant condensed in the first heat exchanger is supplied to the fourth heat exchanger. A fifth heat exchanger installed in the leading refrigerant path;
Is configured to circulate the liquid between the first heat exchanger and the third heat exchanger; and the fifth heat exchanger is configured to circulate the refrigerant condensed in the first heat exchanger. Configured to cool; dehumidifier. 3. The dehumidifier according to claim 2, wherein the second heat exchanger and the fifth heat exchanger are arranged in parallel in the flow of the regeneration air.