JP2000065395A - Dehumidifying air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve COP and constitute so as to be compact, further, permit heating operation. SOLUTION: A humidifying air conditioner is provided with a first switching mechanism 265 for switching selective connecting relations of the suction port 260a of a refrigerant compressor 260 and the discharging port 260b of the same to a second refrigerant outlet, and inlet port 210b and a third refrigerant outlet and inlet port 220a; and a second switching mechanism 280 for switching the selective connecting relations of a fifth refrigerant outlet and inlet port 230a and a sixth refrigerant outlet and inlet port 240a to a fourth refrigerant outlet and inlet port 220b and the first refrigerant outlet and inlet port 210a. The mode of operation of the dehumidifying air conditioner can be changed by the first and second switching mechanisms.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a dehumidifying air conditioner, and more particularly to a dehumidifying air conditioner capable of switching between cooling and heating using a desiccant.

[0002]

2. Description of the Related Art As shown in FIG. 9, 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 the air conditioning system of FIG. 9, a compression heat pump HP using a compressor 260 is used as a heat pump.
Is used. This air conditioning system desorbs and regenerates moisture in the desiccant by passing through the path of the processing air A to which moisture is adsorbed by the desiccant rotor 103 and passing through the desiccant rotor 103 after being heated by the heating source and adsorbing the moisture. A sensible heat exchanger having a path for the regeneration air B, between the treated air to which moisture has been adsorbed and the regeneration air before regenerating the desiccant (desiccant) of the desiccant rotor 103 and before being heated by the heating source. An air conditioner having an air conditioner 104; and a compression heat pump HP. The regeneration air of the air conditioner is heated by a heater 220 using a high heat source of the compression heat pump HP as a heating source to regenerate the desiccant, and the compression heat pump HP The process air of the air conditioner is cooled by the cooler 210 using the low heat source as a cooling heat source.

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. In addition, the regeneration air between the sensible heat exchanger 104 and the heater 220 and the desiccant rotor 10
The heat exchanger 121 with the regenerated air exiting from No. 3 is provided to further enhance the energy saving effect.

The operation of the desiccant air conditioner shown in FIG. 9 will now be described with reference to a psychrometric chart shown in FIG. In FIG. 10, alphabets K to P and Q to X indicate the state of air. This symbol corresponds to the alphabet circled in the flowchart of FIG.

[0005] In FIG. 10, the processing air (state K) from the air-conditioned space 101 is desiccant adsorbed by the desiccant rotor 103 to lower the absolute humidity, and the desiccant heat of adsorption raises the dry-bulb temperature to state L.
Then, in the sensible heat exchanger 104, the air is cooled in the state M while keeping the absolute humidity constant, and enters the cooler 210. Here, the air is further cooled at a constant absolute humidity to become air in the state N, and humidified by the humidifier 105 to lower the dry-bulb temperature to become air in the state P, and is 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, where it cools the processing air to be heated to the state R, enters the heat exchanger 121, and is further heated to the state S. Then, the desiccant is heated by the heater 220 to reach the state T, and the desiccant is regenerated by the desiccant rotor 103. The desiccant itself has a high absolute humidity, the dry-bulb temperature decreases, and the state becomes U. As a result, the temperature of the dry bulb itself is lowered, and the air becomes the state V and is exhausted EX.

Here, the operation of the compression heat pump HP shown in FIG. 9 will be described with reference to the Mollier diagram of FIG.
FIG. 11 is a Mollier diagram of the refrigerant HFC134a. Point a indicates the state of the refrigerant evaporated in the cooler 210,
It is in the state of saturated gas. The pressure is 4.2 kg / cm ² , the temperature is 10 ° C., and the enthalpy is 148.83 kcal / kg.
It is. A state in which this gas is sucked and compressed by the compressor 260,
The state at the discharge port of the compressor 260 is indicated by a point b.
In this state, the pressure is 19.3 kg / cm ² and the temperature is 78
° C and in a superheated gas state. This refrigerant gas is supplied to a heater (a cooler or a condenser when viewed from the refrigerant side) 220
And reaches 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 to reach point d. 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.
/ Kg. 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.

[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, since the sensible heat exchanger generally occupies a large volume in the system, it has made the system configuration difficult and, as a result, the system has to be enlarged.
Further, according to the conventional air-conditioning system as described above, the cooling operation or the dehumidifying operation can be performed, but the heating operation and the defrosting operation required therewith cannot be performed.

Accordingly, an object of the present invention is to provide a dehumidifying air conditioner which has a high COP, is compact, and can perform a heating operation.

[0009]

Means for Solving the Problems In order to achieve the above object, a dehumidifying air conditioner according to the first aspect of the present invention is shown in FIG.
As shown in FIG. 1, a first refrigerant air heat exchanger 210 having a first refrigerant port 210a and a second refrigerant port 210b and exchanging heat between refrigerant and processing air; A refrigerant compressor 260 having a suction port 260a and a discharge port 260b, wherein the second refrigerant port 210b is arranged to be selectively connected to one of the suction port 260a and the discharge port 260b. 2
60; a second refrigerant / air heat exchanger 220 having a third refrigerant inlet / outlet 220a and a fourth refrigerant inlet / outlet 220b and exchanging heat between the refrigerant and the air. A second refrigerant air heat exchanger 220 disposed so that a side not connected to the second refrigerant port 210b is connected to the third refrigerant port 220a; A third refrigerant / air heat exchanger having a fifth refrigerant inlet / outlet 230a and a sixth refrigerant inlet / outlet 240a disposed upstream of the flow of the processing air passing therethrough and exchanging heat between the processing air, the refrigerant and the cooling fluid. 300
A third refrigerant air heat exchanger 300 arranged so that the fourth refrigerant port 220b is selectively connected to one of the fifth refrigerant port 230a and the sixth refrigerant port 240a; A moisture adsorber 103 disposed upstream of the flow of the processing air passing through the third refrigerant air heat exchanger 300 and having a desiccant that adsorbs moisture in the processing air; And the fourth refrigerant port 220 of the sixth refrigerant port 240a.
b is configured to be connected to the first refrigerant port 210a; the third refrigerant air heat exchanger 300 includes a fourth refrigerant port 220b and a fifth refrigerant port 230a. Is connected, the processing air passing through the third refrigerant air heat exchanger 300 is cooled by evaporation of the refrigerant supplied from the fourth refrigerant port 220b to the fifth refrigerant port 230a, and the evaporated refrigerant Is cooled and condensed by the cooling fluid C, and the condensed refrigerant can be supplied to the first refrigerant air heat exchanger 210.

[0010] With this configuration, a third refrigerant air heat exchanger is provided, and the third refrigerant air heat exchanger cools the processing air by evaporating the refrigerant and cools the evaporated refrigerant by the cooling fluid. The heat transfer between the processing air and the cooling fluid can be achieved with a high heat transfer coefficient because the heat transfer can be performed using the evaporation heat transfer and the condensation heat transfer having a high heat transfer coefficient. Further, since the heat transfer between the processing air and the cooling fluid is performed via the refrigerant, the components of the dehumidifying air conditioner can be easily arranged. Further, the refrigerant compressor is arranged such that the second refrigerant port 210b is selectively connected to either the suction port 260a or the discharge port 260b, and the third refrigerant air heat exchanger 300 is connected to the fourth refrigerant air heat exchanger 300. Of the dehumidifying air conditioner can be changed because the refrigerant inlet / outlet 220b is selectively connected to one of the fifth refrigerant inlet / outlet 230a and the sixth refrigerant inlet / outlet 240a.

In the above dehumidifying air conditioner, the suction port 26 of the refrigerant compressor 260 is connected to the second refrigerant port 210b and the third refrigerant port 220a.
A first switching mechanism 265 for switching a selective connection relationship between the first refrigerant port 0a and the discharge port 260b;
and a second switching mechanism 280 that switches a selective connection relationship between the fifth refrigerant port 230a and the sixth refrigerant port 240a to the first refrigerant port 210a and the first refrigerant port 210a.

Further, as described in claim 3, claim 2
In the dehumidifying air conditioner described in the above, the sixth refrigerant port 240a
The refrigerant path between the second switching mechanism 280 and the first
An expansion valve 270 having a second temperature sensing part 275A and a second temperature sensing part 275B; a first temperature sensing part 275A is provided in the refrigerant path between the second refrigerant inlet / outlet 210b and the refrigerant compressor 260. , A second temperature sensing part 275b is provided in the refrigerant path between the refrigerant compressor 260 and the third refrigerant inlet / outlet 220a; the first temperature sensing part 275a and the second temperature sensing part 275b are selectively provided. You may comprise so that switching is possible.

With this configuration, the first temperature sensing section and the second temperature sensing section can be selectively switched.
An appropriate temperature sensing part can be utilized in accordance with the switched operation mode of the present dehumidifying air conditioner.

Further, in the above dehumidifying air conditioner, the regeneration air flows through the second refrigerant air heat exchanger 220 and the second refrigerant air heat exchanger 220 receives the regenerated air. A moisture adsorption device 103 for regenerating the desiccant with the regeneration air is disposed downstream of the regeneration air; a moisture adsorption device 103 disposed upstream of the regeneration air with respect to the second refrigerant air heat exchanger 220. A sensible heat exchanger 121 arranged to exchange heat between the passed regeneration air and the regeneration air before heat exchange in the second refrigerant air heat exchanger 220
Switching the sensible heat exchanger 121 between active and inactive;
The switching mechanism 145 may be provided.

With this configuration, the sensible heat exchanger 12
1, the efficiency of the dehumidifying air conditioner can be increased,
Switching mechanism 14 for activation and deactivation of sensible heat exchanger 121
5, the sensible heat exchanger can be used freely or not depending on the operation mode of the dehumidifying air conditioner.

According to a fifth aspect of the present invention, in the above dehumidifying air conditioner, air is used as the cooling fluid.
When the refrigerant is condensed in the refrigerant air heat exchanger 300, liquid moisture may be supplied together with the air. With this configuration, the temperature of air as a cooling fluid decreases due to heat of vaporization due to evaporation of liquid water,
The cooling effect increases.

A method for operating a dehumidifying air conditioner according to a sixth aspect is the method for operating a dehumidifying air conditioner according to any one of the first to third aspects.
The second refrigerant port 210b and the suction port 260a, the discharge port 260b and the third refrigerant port 220a, the fourth refrigerant port 220b and the fifth refrigerant port 230a, and the sixth refrigerant port 240a and the The first refrigerant port 210a is connected to the first refrigerant port 210a; in the heating operation mode, the second refrigerant port 210b and the discharge port 260b are connected to the suction port 260a.
And the third refrigerant port 220a are connected to the fourth refrigerant port 2a.
20b and the sixth refrigerant port 240a, the fifth refrigerant port 230a and the first refrigerant port 210a are connected to each other, and the third refrigerant air heat exchanger 300 is set in a non-operating state. And By doing so, the cooling operation mode and the heating operation mode can be set reliably.

Further, in this operation method, in the dehumidifying operation mode, the second refrigerant port 210b and the suction port 260a are connected to each other, and the discharge port 260b and the third refrigerant port 220a are connected to each other.
Fourth refrigerant port 220b and fifth refrigerant port 230a
Between the sixth refrigerant port 240a and the first refrigerant port 2
10a may be connected to each other, and the third refrigerant air heat exchanger 300 may be set to a non-operating state; in the defrosting operation mode, the second refrigerant inlet / outlet 210a and the discharge port 260b are connected to each other. Suction port 260a and third refrigerant port 2
20a, the fourth refrigerant port 220b and the sixth refrigerant port 240a, the fifth refrigerant port 230a and the first refrigerant port 210a, respectively, and the flow of the processing air is stopped. You may put it. In this defrosting operation mode, typically, the flow of the regeneration air is also stopped.

Also, as described in claim 7, claim 6
In the operation method described in the above, in the defrosting operation mode, the second refrigerant port and the suction port, the discharge port and the third refrigerant port, the fourth refrigerant port and the sixth The refrigerant port is connected to the fifth refrigerant port and the first refrigerant port.
And the refrigerant inlet / outlet may be connected to each other. Usually, when the heating operation is performed, frost is formed on the heat exchanger as a low heat source. However, if the operation is performed in the defrosting operation mode, the frost can be removed.

[0020]

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 a first embodiment of the present invention, and FIG. 2 is a third embodiment of the present invention used in the air conditioning system of FIG. FIG. 3 is a schematic cross-sectional view showing an example of a refrigerant air heat exchanger, FIG. 3 is a refrigerant Mollier diagram of a heat pump HP1 included in the air conditioning system of FIG. 1, and FIG. 4 is wetness when the air conditioning system of FIG. 1 is operated in a cooling mode. FIG.

Referring to FIG. 1, the structure of the dehumidifying air conditioner according to the first embodiment will be described. This air conditioning system
Mainly, the desiccant (drying agent) is used to lower the humidity of the processing air and maintain the air-conditioned space 101 to which the processing air is supplied in a comfortable environment. In the figure, a blower 102 for circulating the processing air, a desiccant rotor 103 filled with a desiccant, and a third refrigerant air heat exchanger of the present invention (as viewed from the processing air) along the path of the processing air A from the air-conditioned space 101. For example, it is not used as a cooler in the cooling operation mode and is not used as a heat exchanger in the heating operation) 300, a first refrigerant air heat exchanger (a cooler in the cooling operation mode and a heater in the heating operation mode from the viewpoint of the processing air) ) 210 in this order and return to the air-conditioned space 101.

The sensible heat exchanger 121, which is a heat exchanger for exchanging heat between the regeneration air before entering the desiccant rotor 103 and the regeneration air afterward, along the path from the outdoor OA to the regeneration air B, Refrigerant air heat exchanger (as viewed from the side of the regeneration air B, the heater in the cooling operation mode and the defrosting operation mode,
Cooler for heating operation) 220, desiccant rotor 10
3. A blower 140 for circulating the regeneration air and a heat exchanger 121 are arranged in this order, and are configured to exhaust EX to the outside. In addition, a three-way valve 145 as a bypass valve for bypassing the heat exchanger 121 and directly discharging the regeneration air is provided in the regeneration air path between the discharge port of the blower 140 and the heat exchanger 121. ing.

A third refrigerant / air heat exchanger 300 and a blower 160 for circulating the cooling fluid are arranged in this order along the path from the outdoor OA to the outside air as the cooling fluid C, and the air is exhausted outdoors. It is configured to perform EX.

Next, the refrigerant path will be described. In FIG. 1,
The flow of the refrigerant is set in the case of the cooling operation mode.
First, a first refrigerant air heat exchanger (acts as a refrigerant evaporator in the cooling operation mode) 210 along the refrigerant flow path
The refrigerant path 207 connected to the second refrigerant inlet / outlet (acting as a refrigerant gas outlet in the cooling operation mode) 210b is
The first refrigerant-air heat exchanger is connected to a compressor 260 that compresses the refrigerant that has evaporated into gas. Refrigerant compressor 2
60 is a second refrigerant-air heat exchanger (acts as a refrigerant condenser in the cooling operation mode) 220 through the refrigerant path 201.
Is connected to a third refrigerant inlet / outlet (operating as a refrigerant gas inlet in the cooling operation mode) 220a provided in the cooling air supply mode.
Further, a fourth refrigerant inlet / outlet provided in the second refrigerant air heat exchanger (acts as a refrigerant liquid outlet in the cooling operation mode) 2
Reference numeral 20b denotes a third refrigerant air heat exchanger (acting as a processing air cooler in the cooling operation mode) by the refrigerant passage 202.
A throttle 230 is provided in the refrigerant passage 202 or adjacent to the fifth refrigerant port 230a, which is connected to a fifth refrigerant port 230a (acting as a refrigerant liquid inlet in the cooling operation mode) provided at 00. Further, a sixth refrigerant inlet / outlet (acting as a refrigerant liquid outlet in the cooling operation mode) 240a provided in the third refrigerant / air heat exchanger 300 is connected to the first refrigerant / air heat exchanger of the first refrigerant / air heat exchanger by refrigerant paths 230 and 206. (Acting as a refrigerant liquid inlet in the cooling operation mode) 210a. Note that the refrigerant path 2
An expansion valve 270 is provided between 03 and 204.

Here, the refrigerant compressor 260 is connected to the refrigerant inlet 2
60a and a refrigerant discharge port 260b, so that the refrigerant path 207 connected to the second refrigerant port 210b is selectively connected to either the refrigerant suction port 260a or the refrigerant discharge port 260b. Further, a four-way valve 265 serving as a first switching mechanism for connecting the refrigerant path 201 to the refrigerant port of the refrigerant suction port 260a and the refrigerant discharge port 260b that is not connected to the refrigerant path 207 is provided. Is provided. More specifically, the refrigerant suction port 260a
Is connected to the refrigerant path 262, and the refrigerant discharge port 260b is connected to the refrigerant path 261. The four-way valve 265 connects the refrigerant paths 207 and 262, and
01 (cooling operation mode, dehumidification operation mode, defrosting operation mode), communication between the refrigerant paths 207 and 261 and communication between the refrigerant paths 262 and 201 (heating operation mode) Can be selectively switched (see the table in FIG. 7).

In the embodiment shown in FIG. 1, a four-way valve 280 as a second switching mechanism is provided adjacent to the third refrigerant air heat exchanger 300, and the refrigerant path 202 is connected to the third refrigerant air heat exchanger 300. Fifth refrigerant port 230 of refrigerant air heat exchanger 300
a and the sixth refrigerant port 240a, the refrigerant path 206 is further connected to the refrigerant path 202 of the fifth refrigerant port 230a and the sixth refrigerant port 240a. So that it is connected to the refrigerant inlet / outlet. More specifically, a refrigerant path 205 is connected to the fifth refrigerant port 230a, a refrigerant path 204 is connected to the sixth refrigerant port 240a, and a refrigerant path 203 is connected via an expansion valve 270.
The four-way valve 280 connects the refrigerant path 202 and the refrigerant path 205 and connects the refrigerant paths 204 and 203 to the refrigerant path 20.
6 (cooling operation mode, dehumidification operation mode), and communication between the refrigerant paths 202 and 203 and communication between the refrigerant paths 205 and 206 (heating operation mode, defrost operation mode). It is configured such that it can be selectively switched (see the table in FIG. 7).

Here, a three-way valve 145 as a bypass valve
Will be described. An air path 129 is connected to the air inlet side of the three-way valve 145, and an air path 130 </ b> A is connected to one of the two branching outlets to guide air to the heat exchanger 121. An air path 130B is connected to the other of the two outlets, and the air is guided to the exhaust by bypassing the heat exchanger 121. The air path 129 can be selectively switched between communicating with the air path 130A (cooling operation mode, dehumidifying operation mode) and communicating with the air path 130B (heating operation mode, defrosting operation mode). (See table in FIG. 7).

As shown in FIG. 12, 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. ing.
For example, a large number of tubular drying elements 103a are bundled so that the central axis thereof is parallel to the rotation axis AX. The rotor 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 103a, as the rotor 103 rotates,
The processing air A and the regeneration air B are arranged so as to come into contact alternately. In FIG. 12, a part of the outer peripheral portion of the desiccant rotor 103 is shown broken. Although the figure shows a gap between the outer periphery of the desiccant rotor 103 and a part of the drying element 103a, the drying elements 103a are actually bundled and tightly packed in the entire disk. In general, the processing air A (indicated by a white arrow in the figure) and the regeneration air B (indicated by a black solid arrow in the figure) face substantially half of the circular desiccant rotor 103 in parallel with the rotation axis AX. It is configured to flow in a flow format.

The desiccant may be filled in the tubular drying element 103a, the tubular drying element 103a itself may be formed of a desiccant, or the desiccant may be applied to the drying element 103a. The drying element 103a may be made of a porous material, and the material may contain a desiccant. The drying element 103a may be formed in a cylindrical shape having a circular cross section as shown in the figure, or may be formed in a hexagonal cylindrical shape and bundled to form a honeycomb shape as a whole. In any case, the air is configured to flow in the thickness direction of the disk-shaped rotor 103.

Since the heat exchanger 121 must pass a large amount of regeneration air, for example, as shown in FIG. 13, a cross-flow type in which low-temperature regeneration air B1 and high-temperature regeneration air B2 flow orthogonally. A rotary heat exchanger filled with a heat storage material having a large heat capacity is used in place of the drying element in a structure similar to that of the heat exchanger of FIG. At this time, the processing air A in FIG.
1 corresponds to the regeneration air B and the high-temperature regeneration air B2.

Next, referring to FIG. 2, heat pump HP1
The configuration of a heat exchanger as a third refrigerant air heat exchanger suitable for use in the present invention will be described. In the figure, a heat exchanger 300 has a first section 310 through which process air A flows, and a second section 320 through which outside air, which is a cooling fluid, flows. I have.

First section 310, second section and partition 3
A plurality of heat exchange tubes as fluid passages, through which the refrigerant 250 flows, are provided substantially horizontally. In this heat exchange tube, a portion penetrating the first section is an evaporating section 251 (a plurality of evaporating sections are 251A, 251B, and 251C) as a first fluid flow path, and a second section is formed. The portion penetrating is the condensing section 252 (the plurality of condensing sections are 252A, 252B, 252C) as the second fluid flow path.

In the form of the heat exchanger shown in FIG. 2, the evaporating section 251A and the condensing section 252A are formed as an integral flow path by one tube. The same applies to the evaporating sections 251B, C and the condensing sections 252B, C. Therefore, in combination with the fact that the first section 310 and the second section 320 are provided adjacent to each other with one partition wall 301 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 FIG. 2, the evaporating sections are arranged in the order of 251A, 251B, 251C from the top in the figure, and the condensing sections are also 252A, 252A, 2B from the top in the figure.
52B and 252C.

On the other hand, the processing air A is configured to enter the first section in FIG. The outside air, which is a cooling fluid, is configured to enter the second section in the drawing through the duct 171 from below and flow out from above.

Further, in the second section, the upper part thereof, above the heat exchange tube constituting the condensing section 252,
A watering pipe 325 is arranged. Watering pipe 325
Are provided with nozzles 327 at appropriate intervals to condense the water flowing in the watering pipe 325 to the condensing section 2.
It is configured to spray to the heat exchange tube constituting 52.

A vaporizing humidifier 165 is provided at the entrance of the cooling fluid, which is the second fluid, in the second section.
The vaporizing humidifier 165 is made of a material that has a hygroscopic property and a gas permeability, such as a ceramic paper and a nonwoven fabric.

Here, the evaporation pressure in the evaporation section 251 and, consequently, the condensation pressure in the condensation section 252,
That is, the second pressure is determined by the temperature of the processing air A and the temperature of the outside air that is the cooling fluid. The heat exchanger 30 shown in FIG.
No. 0 uses the evaporation heat transfer and the condensation heat transfer, so that the heat transfer coefficient is very excellent and the heat exchange efficiency is very high. In addition, the refrigerant flows from the evaporation section 251 to the condensation section 2.
Since it flows toward 52, that is, it is forced to flow in almost one direction, the heat exchange efficiency between the processing air and the outside air as the cooling fluid is high. Here, the heat exchange efficiency φ means that the inlet temperature of the heat exchanger on the high-temperature side fluid is TP1 and the outlet temperature is T
P2, when the inlet temperature of the heat exchanger of the fluid on the low temperature side is TC1 and the outlet temperature is TC2, when attention is paid to cooling of the fluid on the high temperature side, that is, when the purpose of heat exchange is cooling, φ = (T
P1-TP2) / (TP1-TC1), when attention is paid to heating of a low-temperature fluid, that is, when the purpose of heat exchange is heating,
φ = (TC2−TC1) / (TP1−TC1).

Evaporation section 251, condensation section 2
It is preferable to form a high-performance heat transfer surface by forming a spiral groove such as a linear groove on the inner surface of the barrel of the rifle gun on the inner surface of the heat exchange tube constituting 52. The refrigerant liquid flowing inside usually flows so as to wet the inner surface,
When the spiral groove is formed, the heat transfer coefficient is increased because the boundary layer of the flow is disturbed.

Although the processing air flows through the first section, it is preferable that the fin mounted on the outside of the heat exchange tube is processed into a louver shape so as to disturb the flow of the fluid. Preferably, the fins are similarly configured to disrupt the flow of fluid when the outside air flows into the second compartment but does not spray water. However, when water is sprayed, it is preferable to further provide a corrosion-resistant coating as flat plate fins. This is to prevent corrosive substances possibly mixed in the water from condensing and condensing by evaporation to corrode the fins or tubes. The fins are preferably made of aluminum or copper.

Here, it has been described that the refrigerant flows in one direction from the evaporating section 251 side to the condensing section 252 side. However, for example, a single tube having both ends closed, the evaporating section 251 and the condensing section 252,
Formed as a so-called heat pipe, condensing section 2
The refrigerant condensed in 52 may be returned to the evaporating section 251 by utilizing a capillary phenomenon or the like, where it is evaporated again, and thus the refrigerant may be circulated in one tube. At this time, the heat transfer is still the same using the evaporation heat transfer and the condensation heat transfer, and the heat transfer coefficient can be enjoyed, and the structure becomes simple as a heat exchanger for exchanging heat between the processing air and the cooling fluid. There is an advantage.

The operation of the first embodiment will be described first in the case of the cooling operation mode with reference to FIG. In FIG. 4, the state of air in each part is indicated by alphabetic symbols D, E, K to N, and Q to X. This symbol corresponds to the circled alphabet in the flow diagram of FIG.

First, the flow of the processing air A will be described. In FIG. 4, 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 drying element 103a
Water is adsorbed by the desiccant in (FIG. 12) to lower the absolute humidity, and the dry bulb temperature is raised by the heat of adsorption of the desiccant to reach the state L. This air is treated air path 1
09 through the first section 310 of the process air cooler 300
Where the absolute humidity is constant and evaporation section 2
Cooled by the refrigerant evaporating in 51 (FIG. 2), it becomes air in the state M, and enters the cooler 210 through the path 110.
Here, the air is further cooled at a constant absolute humidity to be in the state N. This air is dried and cooled, and is treated as a treatment air SA having an appropriate humidity and an appropriate temperature as duct 111.
And is returned to the air-conditioned space 101.

Next, the flow of the regeneration air B will be described. In FIG. 4, the regeneration air (state Q) from the outdoor OA is sucked through the regeneration air path 124 and sent to the heat exchanger 121. Here, heat exchange is performed with the high-temperature regenerated air to be exhausted (air in state U described later) to raise the dry-bulb temperature to become air in state R. This air passes through a path 126 and passes through a second refrigerant air heat exchanger (a heater as viewed from the regeneration air) 2
20 and is heated here 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 deprives the desiccant in the drying element 103a (FIG. 12) of water and regenerates it, thereby increasing the absolute humidity and increasing the heat of desiccant moisture desorption. The dry-bulb temperature is lowered to reach the state U. This air is sucked through a passage 128 into a blower 140 for circulating the regeneration air,
9. The heat is sent to the heat exchanger 121 through the three-way valve 145, which is the third switching mechanism, and exchanges heat with the regeneration air (air in the state Q) before being sent to the desiccant rotor 103, as described above. , Itself lowers in temperature to become air in the state V, and is exhausted EX through the passage 130.

Next, the flow of the outside air C as the cooling fluid will be described. The outside air C (state Q) is sent from the outdoor OA to the second section 320 of the process air cooler 300 through the path 171. Here, first, moisture is absorbed by the humidifier 165,
By changing the isenthalpy and increasing the absolute humidity and lowering the dry-bulb temperature, the air becomes state D. State D is almost on the saturation line of the wet vapor diagram. This air is supplied to the second compartment 3
The cooling medium in the condensing section 252 is cooled while absorbing the water supplied by the watering pipe 325 in the inside 20. This air rises in absolute humidity and dry-bulb temperature substantially along the saturation line, becomes air in state E, and is exhausted EX through the passage 172 by the blower 160 provided in the middle of the passage 172.

Referring now to FIG.
5. The operation of the watering pipe 325 will be described. In the air conditioner as described above, as shown in the cycle on the air side shown in the psychrometric chart of FIG. 4, the amount of heat added to the regeneration air for regeneration of the desiccant of the device is pumped from the processing air by ΔH. Assuming that the heat amount is Δq and the driving energy of the compressor is Δh, ΔH = Δq + Δh. The cooling effect ΔQ obtained as a result of the regeneration based on the heat quantity ΔH increases as the temperature of the outside air (state Q) to be heat-exchanged with the treated air (state L) after the adsorption of moisture is lower. That is, it becomes larger as ΔQ−Δq becomes larger in the figure. Therefore, spraying water on the outside air as the cooling fluid is useful for enhancing the cooling effect. In FIG. 4, points indicated as state M ′ and state N ′ conceptually show the positions of state M and state N, respectively, when the vaporizing humidifier 165 and the sprinkling pipe 325 are not used.

Next, the flow of the refrigerant between the devices will be described first with reference to FIG. 1, and then the operation of the heat pump HP1 will be described with reference to FIG.

First, the four-way valve 26 as the first switching mechanism
5. The case where the four-way valve 280 as the second switching mechanism and the three-way valve as the third switching mechanism are set to the cooling operation mode will be described. In FIG. 1, the refrigerant compressor 26
The refrigerant gas compressed by the refrigerant gas is supplied to the second refrigerant air heat exchanger (regeneration air heater, (Refrigerant condenser) 220. Compressor 260
The refrigerant gas compressed in is heated by the heat of compression,
This heat heats the regeneration air in the second refrigerant air heat exchanger 220. The refrigerant gas itself is deprived of heat and condenses.

The refrigerant liquid flowing out of the refrigerant outlet 220b of the second refrigerant air heat exchanger 220 passes through the refrigerant path 202, the second switching mechanism 280, and the refrigerant path 205, and passes through the third refrigerant air heat exchanger 300. To the entrance of the evaporating section 251. In the middle of the refrigerant path 205, the evaporation section 2
In the vicinity of the entrance 51, there is a header.
0 is provided. However, the throttle 230 may be provided in the middle of the coolant path 205 separately from the header.

The liquid refrigerant that has exited the second refrigerant air heat exchanger 220 is decompressed by the throttle 230, expanded, and some of the liquid refrigerant evaporates (flashes). The liquid-gas mixed refrigerant reaches the evaporator section 251 where the liquid refrigerant flows and evaporates to wet the inner walls of the evaporator section tubes to cool the process air flowing through the first compartment.

Evaporation section 251 and condensation section 2
52 is a series of tubes. That is, since the refrigerant gas is configured as an integral flow path, the evaporated refrigerant gas (and the refrigerant liquid that has not evaporated) flows into the condensing section 252 and generates heat by the outside air flowing through the second section and the sprayed water. Deprived and condensed.

At the outlet side of the condensing section 252, a header 240 is provided.
0a is the refrigerant liquid pipe 204, the expansion valve 270, the four-way valve 28
0, the second refrigerant air heat exchanger 2 via the refrigerant path 206
10 is connected. Note that a fixed throttle may be provided in place of the expansion valve 270. In that case, the throttle may be provided, for example, in the header 240 or the refrigerant path 20.
4, 203. That is, the mounting position of the throttle or expansion valve 270 may be anywhere from immediately after the condensing section 252 to the entrance of the second refrigerant air heat exchanger 210, considering only the cooling mode. In consideration of the operation mode, the interval is set immediately after the condensing section 252 to the four-way valve 280. However, if the position is as close as possible to the inlet 210a of the first refrigerant air heat exchanger 210, the throttle or expansion valve 270
After that, the cooling of the piping for the refrigerant considerably lower than the ambient temperature can be minimized. The refrigerant liquid condensed in the condensing section 252 is decompressed and expanded by the throttle or expansion valve 270 to lower the temperature, enters the first refrigerant air heat exchanger 210 and evaporates, and cools the processing air by the heat of evaporation. Restrictors 230 provided before and after the third refrigerant air heat exchanger 300
As the 70, for example, an orifice, a capillary tube, an expansion valve, or the like is used.

In the embodiment shown in FIG. 1, the expansion valve 270 is used as the throttle provided after the third refrigerant air heat exchanger 300. However, as described above, the expansion valve 270 has two temperature sensing parts. Have. In the cooling operation mode shown in FIG. 1, the temperature sensing unit 275A attached to the refrigerant path between the first refrigerant air heat exchanger 210 and the refrigerant compressor 260 is used as the temperature sensing unit.
We make use of one. In the cooling operation mode, the temperature sensing section 275A detects the degree of superheat of the refrigerant gas coming out of the first refrigerant air heat exchanger 210 used as the refrigerant evaporator, and expands the expansion valve so that the refrigerant gas becomes a dry gas. Adjust the opening of 270.

The refrigerant vaporized and gasified in the first refrigerant air heat exchanger 210 passes through the refrigerant path 207, the first switching mechanism 265, and the refrigerant path 262, and passes through the refrigerant compressor 260.
, And the above cycle is repeated.

Next, the operation of the heat pump HP1 in the cooling operation mode will be described with reference to FIG. 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 first refrigerant air heat exchanger 210 of FIG. 1 and is in the state of 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 second refrigerant air heat exchanger 220 and reaches a point c on the Mollier diagram. This point is a state of a saturated gas, and the pressure is 19.3 kg / cm.
^{2. The} temperature is 65 ° C. Under this pressure, it is further cooled and condensed to reach point d. This point is the state of the saturated liquid,
The pressure and temperature are the same as at point c, and the pressure is 19.3 kg / cm
^{2. The} temperature is 65 ° C and the enthalpy is 122.97k
cal / kg.

This refrigerant liquid is decompressed by the throttle 230 and is evaporated by the evaporating section 25 of the processing air cooler 300 which is a heat exchanger.
Flow into 1. On the Mollier diagram, it is indicated by a point e. The temperature will be about 30 ° C. The pressure is set to 4.
2 kg / cm ² and a value between 19.3 kg / cm ^2,
That is, the saturation pressure corresponds to 30 ° C. Here, a part of the liquid is evaporated and the liquid and the gas are mixed. In the evaporating section 251, the refrigerant liquid evaporates under the intermediate pressure and reaches a point f between the saturated liquid line and the saturated gas line at the same pressure. Here, the liquid has almost completely evaporated. At the point e, the ratio between the refrigerant liquid and the gas is the inverse ratio of the difference between the enthalpy at the point where the saturated pressure line at 30 ° C. crosses the saturated liquid line and the saturated gas line and the enthalpy at the point d. As is clear from FIG. 7, the liquid is larger in weight ratio. However,
Since the gas is predominant in volume ratio, the liquid is mixed with a large amount of gas in the evaporating section, and the liquid evaporates while the liquid wets the inner surface of the tube of the evaporating section.

The refrigerant in the state indicated by the point f flows into the condensation section 252. In the condensing section 252, the refrigerant is deprived of heat by the outside air and / or sprayed water flowing through the second compartment and reaches point g. This point is on the saturated liquid line in the Mollier diagram. Temperature 30 ° C, enthalpy 1
It is 09.99 kcal / kg.

The refrigerant liquid at point g is passed through a throttle 240 and
The pressure was reduced to a saturation pressure of 4.2 kg / cm ² ,
As a mixture of the refrigerant liquid and the gas at 10 ° C., the heat reaches the first refrigerant air heat exchanger 210, where it deprives the processing air of heat and evaporates to become a saturated gas in the state of the point a on the Mollier diagram. It is sucked into the compressor 260 and the above cycle is repeated.

As described above, in the third refrigerant air heat exchanger 300, the refrigerant evaporates from the point e to the point f in the evaporating section 251 and evaporates in the condensing section 252.
Since the state changes from the point f to the point g and the heat transfer is the evaporation heat transfer and the condensation heat transfer, the heat transfer coefficient is very high.

Further, the first refrigerant air heat exchanger 210,
When the third refrigerant air heat exchanger 300 is not provided as the compression heat pump including the compressor 260, the second refrigerant air heat exchanger 220, and the expansion valve 270, in the cooling operation mode, the second refrigerant Point d in the air heat exchanger 220
Is returned to the first refrigerant air heat exchanger 210 via the expansion valve 270, the first refrigerant air heat exchanger 2
The enthalpy difference available for 10 is 148.83-12
Whereas there is only 2.97 = 25.86 kcal / kg, in the case of the heat pump HP1 used in the present embodiment provided with the third refrigerant air heat exchanger 300, it is 148.83.
-109.99 = 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%. That is, even if the compressor 260 is of a single-stage type, it can have the same effect as an economizer that is a two-stage type and in which flash gas is sucked into an intermediate stage. Rather, since there is no need to inhale the flash gas into the high pressure stage, a higher COP can be achieved than with the two-stage type.

Next, the case of the dehumidifying operation mode will be described with reference to FIG. In the dehumidifying operation mode, the connection relationship among the first switching mechanism 265, the second switching mechanism 280, and the third switching mechanism 145 is the same as in the cooling operation mode. Also, desiccant rotor 103, blower 102,
The blower 140 and the compressor 260 are operating, but the blower 160 is stopped and the water spray 325 is not operating. At this time, in FIG. 1, the outside air C as the cooling fluid does not flow, and water is not sprayed to the second section 320, so that heat is not taken from the refrigerant between the throttle 230 and the expansion valve 270. . Most transiently, the process air flowing through the first section 310 may heat (or cool) the refrigerant, but eventually the vaporization temperature of the refrigerant between the restrictor 230 and the expansion valve 270 will increase. The temperature will be at the same level as the temperature and will be balanced, so that no heat will flow in and out. Therefore, considering the psychrometric chart of FIG. 4, there is no cooling between the state L and the state M, and the processing air is dehumidified by the desiccant rotor 103 and then cooled by the first refrigerant air heat exchanger 210. Therefore, the state in which the treated air is returned to the air-conditioned space has a lower absolute humidity than the state K, and the dry-bulb temperature is not much different from the state K. That is, this operation mode is basically a dehumidification operation mode.

Next, the heating operation mode will be described with reference to FIG. In the heating operation mode, the first switching mechanism 26
5, the second switching mechanism 280 and the third switching mechanism 145 are connected as shown in FIG. 5 as described above. Further, the blower 102, the blower 140, the compressor 2
60 is operating, but the desiccant rotor 103,
Blower 160 is turned off and water spray 325 is not running. The temperature sensing part of the expansion valve 270 utilizes a temperature sensing part 275B installed in the refrigerant path between the second refrigerant air heat exchanger 220 and the refrigerant compressor 260.

In FIG. 5, the refrigerant discharged from the discharge port 260 b of the refrigerant compressor 260 passes through the refrigerant path 261, the four-way valve 265, and the refrigerant path 207 to the second refrigerant port 2.
The heat is conveyed to a first refrigerant air heat exchanger (which acts as a refrigerant condenser in a heating operation mode) 210 and is condensed by releasing the heat. With this heat, the first air-refrigerant heat exchanger 210 heats the processing air that is in a heat exchange relationship with the refrigerant.

The refrigerant condensed in the first refrigerant air heat exchanger 210 is supplied to the refrigerant path 206, the four-way valve 280, and the refrigerant path 20.
5 to the third refrigerant air heat exchanger 300. In the heating operation mode, since the blower 160 is not operated, the refrigerant does not particularly exchange heat with other fluids.
, The refrigerant path 204, the expansion valve 270, the refrigerant path 203, the four-way valve 2
80, through the refrigerant path 202, a second refrigerant air heat exchanger (acts as a refrigerant evaporator in the heating operation mode) 220
Sent to In the second refrigerant air heat exchanger 220, heat is obtained and evaporated. This heat is obtained from outside air used as regeneration air during cooling. The outside air in heat exchange relation with the refrigerant is cooled by the refrigerant that evaporates in the opposite direction.

The refrigerant evaporated in the second refrigerant air heat exchanger 220 is supplied to the refrigerant path 201, the four-way valve 265, and the refrigerant path 26.
2 to the suction port 260a and the refrigerant compressor 260
Compressed. Thus, the circulation of the refrigerant is repeated. The second temperature sensor 275B of the expansion valve 270 allows the second
The degree of superheat of the refrigerant at the outlet of the refrigerant air heat exchanger 220 is detected, and the expansion valve 2 is set so that the refrigerant gas is in a dry state.
The opening of 70 is adjusted.

The flow of the processing air A in the heating operation mode is the same as that in the cooling operation, but the desiccant rotor 103 is stopped and no dehumidification is performed. The processing air that has passed through the desiccant rotor is heated by the refrigerant in the first refrigerant air heat exchanger 210 to increase the dry bulb temperature,
The air is supplied to the air-conditioned space 101 as air having an appropriate dry bulb temperature. Note that a humidifier (not shown) may be provided between the heat exchanger 210 and the air-conditioned space 101 for the heating operation.

The flow of outside air B in the heating operation is the same as that in the cooling operation except that the third switching mechanism 145 bypasses the heat exchanger 121. Since heat exchange is not performed in the heat exchanger 121, the outside air passes through the heat exchanger 121 and reaches the second refrigerant air heat exchanger 220, and the second refrigerant air heat exchanger 220 evaporates the refrigerant to form itself. Is cooled and reaches the desiccant rotor 103. Since the desiccant rotor 103 is stopped, no water is exchanged here, and the desiccant rotor 103 passes through the blower 140 and is exhausted.

Next, the defrosting operation mode will be described with reference to FIG. In the defrosting operation mode, the first switching mechanism 26
5, the second switching mechanism 280 and the third switching mechanism 145 are connected as shown in FIG. The blower 160 and the compressor 260 are operated, but the desiccant rotor 103, the blower 102,
Blower 140 is normally shut off and water spray 325 is not running. As the temperature sensing part of the expansion valve 270, the temperature sensing part 2
75A is utilized. The blowers 102 and 140
May be driven.

In FIG. 6, the refrigerant discharged from the discharge port 260 b of the refrigerant compressor 260 passes through the refrigerant path 261, the four-way valve 265, and the refrigerant path 201 to the third refrigerant port 2.
The heat is discharged to the second refrigerant / air heat exchanger 220 and condensed. With this heat, the second refrigerant air heat exchanger 2
The frost adhering to the heat transfer surface on the air side of 20 is melted or sublimated to be defrosted. The refrigerant condensed in the second refrigerant air heat exchanger 220 passes through the refrigerant path 202, the four-way valve 280, the refrigerant path 203, the expansion valve 270, and the refrigerant path 204.
It is sent to the third refrigerant air heat exchanger 300. In the defrosting operation mode, since the blower 160 is operating and water is not sprayed, the refrigerant exchanges heat with the outside air C to obtain heat and evaporate. The evaporated refrigerant passes through the refrigerant passage 205 and the four-way valve 2.
80, is sent to the first refrigerant air heat exchanger 210 through the refrigerant path 206. In the defrosting operation mode, the blower 10
2 is stopped, the first refrigerant air heat exchanger 21
At 0, the refrigerant path 207 passes without heat exchange,
The refrigerant compressor 26 passes through the four-way valve 265 and the refrigerant path 262.
Returning to 0, the above refrigerant circulation is repeated. The expansion valve 2
The degree of superheat of the refrigerant at the outlet of the third refrigerant air heat exchanger 300 is detected by the temperature sensing part 275A of 70, and the opening of the expansion valve 270 is adjusted so that the refrigerant gas is in a dry state. . As described above, in the defrosting operation, the heat pump HP1
Pumps heat from the outside air C to produce a second refrigerant air heat exchanger 2
20 frosts can be removed. Therefore, a large amount of heat can be pumped up and defrosted in a short time, and the defrosting time can be shortened.

Further, in the defrosting operation mode, the blower 10
2 is not operating, the processing air A is not circulating, and since the blower 140 is not operating, the regeneration air B is not circulating. Therefore, in this embodiment, the processing air is not cooled in the defrosting operation mode, so that the heating effect can be maintained at a high level, and the person in the air-conditioned space 101 does not feel uncomfortable.

The operation of each device in each operation mode has been described above. The table in FIG. 7 shows each operation mode and operation of each device of the dehumidifying air conditioner according to the first embodiment of the present invention. It is summarized. As shown in the table, the dehumidifying air conditioner of the first embodiment can operate in a cooling operation mode, a dehumidification operation mode, a heating operation mode, and a defrost operation mode.
The operation and stop state of the main equipment in each operation mode, the connection relation of each switching mechanism, the temperature sensing part used by the expansion valve are:
As described above.

Referring to FIG. 8, an example of the mechanical arrangement of the dehumidifying air conditioner described above will be described. In FIG. 8, devices constituting the apparatus are accommodated in a cabinet 700. The cabinet 700 is formed as a rectangular parallelepiped housing made of, for example, a thin steel plate, and has a suction opening for the processing air RA opened at the lower side in the vertical direction. A filter 501 is provided at the opening to prevent dust from the air-conditioned space from being brought into the device. The blower 102 is installed in the cabinet 700 inside the filter 501, and the suction port thereof communicates with the processing air suction port of the cabinet through the filter 501.

A compressor 260 and a blower 140 are arranged in the space below the cabinet so as to be arranged substantially horizontally in the horizontal direction. A four-way valve 265 is installed near the compressor 260. Further, above the compressor 260 and the blower 140, the desiccant rotor 103 is arranged with the rotation axis directed vertically. Desiccant rotor 1
Reference numeral 03 denotes an electric motor 105, which is a driving machine also arranged in the vicinity thereof with the rotation axis directed in the vertical direction, and is connected to the electric motor 105 by a belt, a chain, or the like, and is configured to be rotatable at a low speed of about one rotation in a few minutes. . As described above, when the desiccant rotor 103 is arranged so as to rotate in a substantially horizontal plane around a rotation axis oriented in the vertical direction, the height of the entire apparatus can be suppressed low, and the apparatus is compactly assembled. In addition, if most of the blowers 102 and 140, which are movable elements or rotating bodies, including the heavy compressor 260, and the desiccant rotor 103 are collected in the lower part of the apparatus, the lower part of the cabinet 700, that is, near the foundation, the influence of vibration will be reduced. And the installation stability of the device is increased.

The outlet of the blower 102 is connected to the desiccant rotor 103 through a passage 108. Passage 108
Is formed so as to be separated from other parts by, for example, a thin steel plate similar to that forming the cabinet 700. The processing air flows into an area of about half (semicircle) of the circular desiccant rotor 103.

Vertically above the desiccant rotor 103,
In particular, above the half (semicircle) region where the process air flows, the first section 31 of the third refrigerant air heat exchanger 300
0, that is, the evaporation section 251 is arranged. The path 109 connecting the desiccant rotor 103 and the first section 310 is, in the structure of FIG. 8, a horizontally placed rotor and also horizontally placed evaporation section tubes (and fins attached to these tubes). And is formed as a narrow space between them.

Above the first section 310 in the vertical direction, a first refrigerant air heat exchanger 210 is arranged with its cooling pipe horizontal. In the example shown in FIG. 8, the path 110 is a space between the first section 310 and the first refrigerant air heat exchanger 210, but since both are arranged closely,
The space hardly exists. Above the first refrigerant air heat exchanger 210 in the vertical direction, an opening for blowing the supply air SA into the air-conditioned space is provided in the cabinet 700.

On the other hand, an outside air OA introduction port is opened at an upper portion of the cabinet 700 on the side opposite to the processing air inlet, and a filter 502 for blocking outside dust is provided here. I have. The space inside the filter 502 constitutes the path 124, and the cross-flow type heat exchanger 121 is installed so as to define a part of the space 124. A second refrigerant air heat exchanger 220 is arranged on one outlet side of the heat exchanger 121. The second refrigerant air heat exchanger 220 has a heat exchanger tube disposed substantially horizontally and is disposed substantially side by side with the first refrigerant air heat exchanger 210. The space below the second refrigerant air heat exchanger 220 in the vertical direction and between the desiccant rotor 103
7 through which the desiccant rotor 1
With respect to the above-mentioned half of the process air 03, the regeneration air is guided to the other half. A space vertically below a half area of the desiccant rotor 103 through which the regeneration air passes forms a path 128, and a blower 140 is installed in this space with its suction port facing the space. The outlet of the blower 140 faces sideward, and is connected to the heat exchanger 121 by a path 129 defined in the cabinet 700 in a vertical direction. The regenerated air passing therethrough is defined by the heat exchanger 121 and the cabinet 700 in the heat exchanger 121 through a flow path orthogonal to the flow path of the air guided through the path 124 described above. To the path 131 which is a space
Exhaust EX through opening in cabinet 700
Is done.

Here, an exhaust port is opened in the cabinet 700 at the uppermost part of the path 129, and a hinge is provided to selectively open or close the opening and the regeneration air inlet from the path 129 of the heat exchanger 121. A lid for exercise is provided. This lid acts as a three-way valve 145. That is, the flow of the path 129 is selectively communicated with the heat exchanger 121 or the outside air.

Further, an outside air OA intake port is opened on the side of the cabinet 700 and almost immediately above the intake port of the processing air RA. A filter 503 is provided in this opening to prevent outside dust from being brought into the apparatus.
The space inside the filter 503 forms a path 171, and a humidifier 165 is provided substantially horizontally above this space. The space above the humidifier 165 constitutes a second compartment 320 in which the heat exchange tubes of the condensation section 252 are arranged substantially horizontally. The condensing section 252 and the evaporating section 251 described above are constituted by an integral tube. A watering pipe 325 is disposed in a space above the condensing section 252 so that water can be sprayed from above the tubes (and fins) of the condensing section 252. The watering pipe 325 is provided with a control valve, and is configured to appropriately adjust the amount of water to be sprayed. For example, the humidifier 165 is adjusted to be moderately moist and not too moist. In addition, the lower part of the space constituting the path 171 is a drain pan, and is configured so that excess water can be discharged to the outside of the cabinet 700 when water is excessively sprayed with a watering pipe. Second section 32
The space above the vertical direction 0 is also the path 172, and an air outlet is opened in the portion of the cabinet 700 above this space. A blower 160 is provided at the air outlet.

On the other hand, the four-way valve 26
The refrigerant pipe 201 for sending the refrigerant gas discharged from the compressor 260 to the second refrigerant air heat exchanger 220 from the four-way valve 265 (in the cooling operation mode) extends horizontally across the bottom of the cabinet 700. Crawling up and standing up further. A four-way valve 280 is installed in the regeneration air path 131 above the second refrigerant air heat exchanger 220, and a throttle (also serving as a refrigerant header) 230 is provided below the four-way valve 280. The condensed refrigerant is decompressed to reduce the pressure of the condensed refrigerant to the evaporation section 25 of the third refrigerant air heat exchanger 300.
Lead to 1. The refrigerant decompressed via the throttle is sent to the evaporation section 251 composed of a plurality of tubes and evaporates. A header 240 for collecting the refrigerant condensed in the condensing section 252 is provided at the outlet of the condensing section 252. The refrigerant pipe from the header 240 rises from the header 240 and is decompressed by an expansion valve 270 provided near the uppermost portion. The aperture may be provided in the header 240 and the aperture 270 in FIG. 8 may be omitted. At this time, it is necessary to sufficiently maintain the cooling from the pressure reduction by the throttle 240 to the first refrigerant air heat exchanger 210 via the four-way valve 280.

The refrigerant pipe 207 connecting the first refrigerant air heat exchanger 210 and the compressor 260 via the four-way valve 265
Are disposed vertically downward from the first refrigerant air heat exchanger 210. The opening of the throttle 270 (in the cooling operation mode) is adjusted by a temperature controller having a temperature-sensitive portion attached to the refrigerant gas pipe at the outlet of the first refrigerant air heat exchanger 210, that is, the degree of throttle is adjusted. You may. In this way, the excess refrigerant liquid is removed from the first refrigerant air heat exchanger 210.
, And as a result, the liquid refrigerant can be prevented from being sucked into the compressor 260.

[0085]

As described above, according to the present invention, a third refrigerant air heat exchanger is provided, and a suction port and a discharge port of a refrigerant compressor are provided to the second refrigerant port and the third refrigerant port. And the selective connection relationship between the fourth refrigerant port and the first refrigerant port, and between the fifth refrigerant port and the sixth refrigerant port, can be switched. It is possible to provide a compact and compact dehumidifying air conditioner capable of cooling operation and heating operation, having a high COP.

[Brief description of the drawings]

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

FIG. 2 is a schematic sectional view of a heat exchanger suitable for use in a heat pump used in 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 psychrometric chart for explaining the operation of the dehumidifying air conditioner of FIG. 1;

FIG. 5 is a flowchart when the dehumidifying air conditioner according to the first embodiment of the present invention is operated in a heating operation mode.

FIG. 6 is a flowchart when the dehumidifying air conditioner according to the first embodiment of the present invention is operated in a defrosting operation mode.

FIG. 7 is a table showing an operation mode of a dehumidifying air conditioner according to an embodiment of the present invention and an operation of each device.

FIG. 8 is a schematic front sectional view showing an example of the actual structure of the dehumidifying air conditioner according to the first embodiment of the present invention.

FIG. 9 is a flowchart of a conventional dehumidifying air conditioner.

FIG. 10 is a psychrometric chart for explaining the operation of the conventional dehumidifying air conditioner shown in FIG.

FIG. 11 is a Mollier diagram of a heat pump used in the conventional dehumidifying air conditioner shown in FIG.

FIG. 12 is a perspective view showing an example of the structure of a desiccant rotor.

FIG. 13 is a perspective view showing an example of a cross-flow heat exchanger.

[Explanation of symbols]

 101 air conditioning space 102, 140, 160 blower 103 desiccant rotor 121 heat exchanger 165 evaporative humidifier 210 first refrigerant air heat exchanger 220 second refrigerant air heat exchanger 230 header throttle 240 header 251 evaporating section 252 condensation section 260 Compressor 300, 300b Third refrigerant air heat exchanger 310 First section 320 Second section 325 Watering pipe 470 Cooling tower 501, 502, 503 Filter 700 Cabinet HP, HP1 Heat pump

Claims (7)

[Claims] A first refrigerant air heat exchanger having a first refrigerant port and a second refrigerant port for exchanging heat between the refrigerant and the processing air; a suction port for sucking and discharging the refrigerant and a discharge port, respectively. A refrigerant compressor having an outlet, the refrigerant compressor being arranged such that the second refrigerant port is selectively connected to one of the suction port and the discharge port; and a third refrigerant port. And a fourth refrigerant inlet / outlet, and a second refrigerant / air heat exchanger for exchanging heat between refrigerant and air, wherein the second refrigerant air inlet / outlet is not connected to the second refrigerant inlet / outlet. A second refrigerant air heat exchanger disposed so as to be connected to the third refrigerant inlet / outlet; and a second refrigerant air heat exchanger disposed upstream of a flow of processing air passing through the first refrigerant air heat exchanger. Heat exchange between the processing air, the refrigerant and the cooling fluid,
A third refrigerant air heat exchanger having a fifth refrigerant port and a sixth refrigerant port, wherein the fourth refrigerant port is any one of the fifth refrigerant port and the sixth refrigerant port. A third refrigerant air heat exchanger arranged to be selectively connected; and a third refrigerant air heat exchanger arranged upstream of the flow of the processing air passing through the third refrigerant air heat exchanger, A moisture adsorbing device having a desiccant for adsorbing moisture; the fifth refrigerant port and the sixth refrigerant port which are not connected to the fourth refrigerant port are connected to the first refrigerant port. The third refrigerant air heat exchanger, when the fourth refrigerant port and the fifth refrigerant port are connected,
The process air passing through the third refrigerant air heat exchanger is cooled by evaporation of the refrigerant supplied from the fourth refrigerant port to the fifth refrigerant port, and the evaporated refrigerant is cooled by a cooling fluid. The dehumidifying air conditioner is configured to be capable of supplying condensed and condensed refrigerant to the first refrigerant air heat exchanger. 2. A first switching mechanism for switching a selective connection relationship between the suction port and the discharge port of the refrigerant compressor to the second refrigerant port and the third refrigerant port, and And a second switching mechanism for selectively switching a connection relationship between the fifth refrigerant port and the sixth refrigerant port between the fourth refrigerant port and the first refrigerant port; Item 2. A dehumidifying air conditioner according to item 1. 3. An expansion valve having a first temperature sensing portion and a second temperature sensing portion in a coolant path between the sixth coolant inlet / outlet and the second switching mechanism; Is provided in a refrigerant path between the second refrigerant port and the refrigerant compressor, and the second temperature part is provided between the refrigerant compressor and the third refrigerant port. The dehumidifying air conditioner according to claim 2, wherein the first temperature sensing section and the second temperature sensing section are selectively switchable. 4. A method for flowing regeneration air through the second refrigerant air heat exchanger, and regenerating the desiccant with the regeneration air downstream of the regeneration air with respect to the second refrigerant air heat exchanger. A moisture adsorber is disposed; the regenerated air passing through the moisture adsorber, which is disposed on the upstream side of the regenerated air with respect to the second refrigerant air heat exchanger, and the second refrigerant air heat exchanger; A sensible heat exchanger arranged to exchange heat with regenerated air before heat exchange; and a switching mechanism for switching the sensible heat exchanger between an active state and an inactive state; The dehumidifying air conditioner according to any one of claims 1 to 3. 5. The method according to claim 1, wherein air is used as the cooling fluid, and when the refrigerant is condensed in the third refrigerant air heat exchanger, liquid moisture is supplied together with the air. Any one of claims 1 to 4
The dehumidifying air conditioner according to Item. 6. In the cooling operation mode, the second refrigerant port and the suction port are connected to each other, the discharge port and the third refrigerant port are connected to each other, and the fourth refrigerant port and the fifth refrigerant port are connected to each other. Connecting the sixth refrigerant port and the first refrigerant port; respectively, in the heating operation mode, connecting the second refrigerant port and the discharge port with the suction port and the third refrigerant port; Connect the fourth refrigerant port and the sixth refrigerant port, and connect the fifth refrigerant port and the first refrigerant port, respectively, and deactivate the third refrigerant air heat exchanger. The method for operating a dehumidifying air conditioner according to any one of claims 1 to 3, wherein the method is placed in a state. 7. Further, in the defrosting operation mode, the second refrigerant port and the suction port, the discharge port and the third refrigerant port, the fourth refrigerant port and the sixth refrigerant are connected. The operating method according to claim 6, wherein an inlet / outlet is connected to the fifth refrigerant inlet / outlet and the first refrigerant inlet / outlet, respectively.