JP2010151376A - Air conditioner and air conditioning system - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an outside air treating air conditioner of high dehumidifying/humidifying capacity and high efficiency, dispensing with a dew condensation treating structure of a heat exchanger and switching operation on the air circuit side. <P>SOLUTION: The air conditioner has: a total heat exchanger for exchanging heat between air flowing in an outside air lead-in line A and air flowing in an exhaust release line B; a refrigerant circuit composed of a compressor, a four way valve, an expansion valve, a condenser and a plurality of evaporators; and a moisture adsorbing means. The total heat exchanger, the condenser, a regeneration area of the moisture adsorbing means, and the evaporators, are arranged in sequence from the windward side of the exhaust release line B toward the leeward side. The total heat exchanger, the condenser, the regeneration area of the moisture adsorbing means, and the evaporators are arranged in sequence from the windward side of the outside air lead-in line A toward the leeward side by switching the refrigerant circuit. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an air conditioning apparatus and an air conditioning system using a desiccant.

  2. Description of the Related Art Conventionally, air conditioning systems that perform external air processing and ventilation air conditioning by combining a total heat exchanger, a heat pump, and a desiccant are known. In the configuration of the conventional invention, a heat pump and a desiccant are arranged after the total heat exchanger, the outside air and the room air are introduced into the total heat exchanger to exchange the total heat, and then sent to the heat pump. The air path structure adjusts the humidity (for example, see Patent Documents 1 and 2).

Japanese Patent Laid-Open No. 10-197011 (page 3-4, FIG. 2) Japanese Patent Laid-Open No. 10-205820 (FIG. 1)

  However, in the conventional invention, the condenser is disposed upstream of the desiccant regeneration side, and the evaporator is disposed downstream of the desiccant adsorption side. For example, during cooling operation, the regeneration exhaust heat of the desiccant is not generated. Since the exhaust gas is discharged as it is to the outside as it is, there is a problem that the regeneration exhaust heat is not effectively used (for example, Patent Documents 1 and 2).

  In addition, in order to increase the desiccant adsorption / desorption capability, it is necessary to increase the regeneration air temperature. For this purpose, it is necessary to increase the high-pressure side refrigerant condensation temperature of the heat pump, which increases the load of the heat pump. There has been a problem of lowering.

  In the conventional invention, the condenser is disposed upstream of the regeneration side of the desiccant, and the evaporator is disposed downstream of the regeneration side of the desiccant. Therefore, the evaporator is not disposed upstream of the adsorption side of the desiccant. Since the side air flows freely, there is a problem that the capacity of the desiccant to absorb and desorb is greatly influenced by the state of the suction side inflow air (for example, Patent Documents 1 and 2).

  Further, in the conventional invention, when switching between the operation for dehumidifying the room and the operation for humidification, the circuit on the refrigerant circuit side is switched without switching the circuit on the air air passage side, but the refrigerant-air heat exchange is performed. Since the heat exchangers (4) are stopped except for the heat exchangers (2) required for each operation of dehumidification / humidification, the other heat exchanger (2) is not effectively used. (For example, Patent Document 2). Further, there has been a problem that there is no air conditioning apparatus that does not generate drain for the condensation treatment in the evaporator and has high dehumidifying / humidifying performance in the desiccant.

  The present invention has been made to solve the above-described problems, and an object thereof is to provide an air conditioning apparatus and an air conditioning system that have high desiccant / humidifying performance in a desiccant and are efficient.

  An air conditioner according to the present invention includes a first air flow path that forms a flow of air from the outdoor to the indoors, a second air flow path that forms a flow of air from the indoors to the outdoor, Arranged across the air flow path and the second air flow path, dehumidifying when located in either one of the first air flow path or the second air flow path, and located in either one A moisture adsorbing means that is regenerated by heating, and alternately repeats the adsorption dehumidification and heating regeneration operations performed in the first air flow path and the second air flow path, and the first air flow path and the first air flow path. A plurality of heat exchangers disposed on the upstream side and the downstream side of each of the moisture adsorbing means arranged in the air flow of the two air flow paths, and circulating a refrigerant to the plurality of heat exchangers in the compressor, Provided in the first air flow path and the second air flow path, A refrigerant circuit having a throttling device and a four-way valve for switching the flow of refrigerant so that one of the heat exchangers arranged upstream of this is a condenser and the other is a first evaporator; A circuit for branching the refrigerant flowing to the evaporator to a heat exchanger disposed on the downstream side of each of the moisture adsorbing means disposed in both the first air flow path and the second air flow path. And a refrigerant branch circuit that operates the downstream side of the condenser as the second evaporator and the downstream side of the first evaporator as the third evaporator and returns it to the compressor.

  In the air conditioner according to the present invention, a condenser is disposed upstream of the regeneration side of the moisture adsorbing means (same as the desiccant), and an evaporator is disposed downstream. Therefore, upstream of the regeneration side, the release of warm heat of the refrigerant in the condenser is promoted, and the air flowing into the moisture adsorbing means is heated. On the other hand, at the downstream side of the regeneration side, the refrigerant sucked by the compressor is warmed by the air that has passed through the moisture adsorbing means, and the air that has passed through the moisture adsorbing means is cooled. It is possible to obtain an air conditioner that can increase the efficiency of the heat pump and improve the efficiency of the heat pump.

Embodiment 1 FIG.
"System configuration"
1 to 4 illustrate the air-conditioning apparatus according to Embodiment 1 of the present invention. FIG. 1 is a configuration diagram schematically showing an air path configuration in a cooling and dehumidifying operation mode, and FIG. FIG. 2A is a block diagram schematically showing the air path configuration in the operation mode, FIG. 2A is a humid air line diagram showing the movement of the operating state in the outside air introduction path A during cooling dehumidification, and FIG. It is a humid air line figure which shows the movement of the operating state in the exhaust discharge path | route B at the time. 4A is a wet air diagram showing the movement of the operating state in the outside air introduction path A during heating humidification, and FIG. 4B is the wetness showing the movement of the operating state in the exhaust discharge path B during heating humidification. It is an air diagram. 2 and 4, the vertical axis represents absolute humidity, and the horizontal axis represents dry bulb temperature. Moreover, the states 1 to 10 indicating the air state correspond to the numbers 1 to 10 circled in FIGS. 2 and 4, respectively.

  1 and 3, the air conditioner includes a compressor 1, a four-way valve 2a, expansion valves 3a, 3b, and 3c, check valves 4a and 4b, a first heat exchanger 5a, and a second heat exchanger 5b. A refrigerant circuit composed of the third heat exchanger 5c and the fourth heat exchanger 5d, an air path A that is an outdoor air introduction path from the outdoor to the indoor, and an air path that is an exhaust discharge path from the indoor to the outdoor Moisture adsorption with a total heat exchanger 10 arranged across B and exchanging sensible heat and latent heat of both air paths with each other and a rotating desiccant rotor arranged over both air paths, for example. And a moisture adsorption means 20 that repeats release (regeneration). Moreover, the sensor 7 which can detect temperature and humidity is provided in the downstream of each heat exchanger, and the sensor 6 which can detect the refrigerant | coolant temperature in each heat exchanger is provided.

  The first heat exchanger 5a is connected in series with the second heat exchanger 5b via the expansion valve 3a, and the first heat exchanger 5a is a condenser and a second heat exchanger during the cooling and dehumidifying operation. 5b operates as a first evaporator (FIG. 1), and is configured so that the second heat exchanger 5b operates as a condenser and the first heat exchanger 5a operates as a first evaporator during the heating and humidifying operation. (FIG. 3). An expansion valve 3b, a third heat exchanger, an expansion valve 3c, and a fourth heat exchanger are provided so as to be connected in parallel with the first evaporator, respectively. The heat exchanger 5c operates as a second evaporator and the fourth heat exchanger 5d operates as a third evaporator (FIG. 1). During the heating and humidifying operation, the third heat exchanger 5c is operated as the third evaporator. The fourth heat exchanger 5d is configured to operate as a second evaporator (FIG. 3). In this embodiment, the role of the three evaporators whose roles are changed between the cooling and dehumidifying operation and the heating and humidifying operation is as follows. The first evaporator, the evaporator located on the regeneration side leeward is defined as the second evaporator, and the evaporator located on the adsorption side leeward is defined as the third evaporator.

  The check valves 4a and 4b have an inlet side of the check valve 4a between the first heat exchanger 5a and the expansion valve 3a, and an inlet of the check valve 4b between the second heat exchanger 5b and the expansion valve 3a. A side is provided. And after each outlet side merges once, it branch-connects to the expansion valves 3b and 3c. Further, a third heat exchanger 5c is connected downstream of the expansion valve 3b, and a fourth heat exchanger 5d is connected downstream of the expansion valve 3c, and the third heat exchanger 5c and the fourth heat exchanger are connected. The outlet side of the exchanger 5d joins and is connected to the suction side of the compressor 1.

  The moisture adsorption means 20 is, for example, a desiccant rotor. The desiccant rotor is a honeycomb-structured rotor having air permeability in the axial direction, and has a rotating mechanism such as a motor. An adsorbent is supported on the surface of the rotor in contact with the air, and moisture adsorption and release can be repeated. In addition, as long as the mechanism which plays the same role is provided, it is not limited to this form. The desiccant rotor uses, for example, zeolite, silica gel, activated carbon or the like as an adsorbent, and is applied, surface-treated or impregnated on a porous rotor base material. The adsorbent may be supported on the rotor by the entire rotor, or only a part of the rotor may be ventilated.

  In addition, although the ratio of the adsorption | suction side area | region in the moisture adsorption means 20 and the reproduction | regeneration side area | region is set to 1: 1 in this invention, you may change into arbitrary ratios.

  Refrigerant used in the refrigerant circuit is not limited, natural refrigerants such as carbon dioxide, hydrocarbons, helium, refrigerants not containing chlorine such as HFC410A, HFC407C, or R22 used in existing products, Fluorocarbon refrigerant such as R134a. And various types, such as a reciprocating machine, a rotary, a scroll, a screw, are applicable to fluid apparatuses, such as a compressor which circulates this refrigerant | coolant.

In the air conditioner, the outside air introduction path A (first air flow) for introducing outside air (indicated by the symbol “OA” in the figure) into the room as indoor introduction air (indicated by the symbol “SA” in the figure). And an exhaust discharge path B (second air flow) that discharges indoor air (indicated by the symbol “RA” in the figure) to the outside as exhaust (indicated by the symbol “EA” in the figure). (Corresponding to the road). The outside air introduction path A and the exhaust discharge path B (hereinafter, collectively or one may be referred to as an air path or an air flow path) are each provided with a blowing means (not shown) such as a fan, for example. Air flows in each of the air paths. The total heat exchanger 10 and the moisture adsorption means 20 are provided across both air paths, and a refrigerant circuit is provided as a heat source for assisting and promoting the adsorption and desorption of the moisture adsorption means 20.
<Operation description of refrigerant circuit>

  Next, the operation switching operation between the cooling / dehumidifying operation and the heating / humidifying operation of the refrigerant circuit will be described. Switching between the cooling and dehumidifying operation and the heating and humidifying operation is performed by switching the four-way valve 2a and the check valves 4a and 4b.

(Cooling and dehumidifying operation mode)
In the cooling and dehumidifying operation (FIG. 1), the four-way valve 2a is set to be connected to the discharge side of the compressor 1 and the first heat exchanger 5a. The first heat exchanger 5a operates as a condenser, and the refrigerant that has passed through the expansion valve 3a is depressurized to a low temperature and a low pressure and then flows into the second heat exchanger. Here, the second heat exchanger operates as a first evaporator. At this time, since a large differential pressure is generated before and after the expansion valve 3a, the differential pressure acts on the check valve 4b in the reverse direction to be “closed”, and a differential pressure is generated in the check valve 4a in the forward direction. Open ". Then, the high-temperature and high-pressure refrigerant that has passed through the check valve 4a is branched into two, is decompressed by the expansion valves 3c and 3d, becomes low-temperature and low-pressure, and flows into the third heat exchanger and the fourth heat exchanger, respectively. Here, the third heat exchanger operates as a second evaporator, and the fourth heat exchanger operates as a third evaporator. The refrigerant that has passed through each evaporator returns to the suction side of the compressor 1.

(Heating and humidifying operation mode)
In the heating and humidifying operation (FIG. 3), the four-way valve 2a is set to be connected to the discharge side of the compressor 1 and the second heat exchanger 5b. The second heat exchanger 5b operates as a condenser, and the refrigerant that has passed through the expansion valve 3a is depressurized to a low temperature and a low pressure, and then flows into the first heat exchanger 5a. Here, the first heat exchanger operates as a first evaporator. At this time, since a large differential pressure is generated before and after the expansion valve 3a, the differential pressure acts in the reverse direction on the check valve 4a to be “closed”, and the differential pressure is generated in the forward direction on the check valve 4b. Open ". Then, the high-temperature and high-pressure refrigerant that has passed through the check valve 4b is bifurcated and depressurized by the expansion valves 3c and 3d to become low-temperature and low-pressure, and flows into the third heat exchanger and the fourth heat exchanger, respectively. Here, the third heat exchanger operates as a third evaporator, and the fourth heat exchanger operates as a second evaporator. The refrigerant that has passed through each evaporator returns to the suction side of the compressor 1.
《Explanation of air side circuit operation》
Next, the operation of the air side circuit in each operation mode will be described.
(Cooling and dehumidifying operation mode)
In the cooling and dehumidifying operation (FIGS. 1 and 2), in the outside air introduction path A of the air conditioner, after the introduced air introduced from the outside air OA is dehumidified by the total heat exchanger 10, the second heat exchanger 5b ( First evaporator). Here, the introduced air is cooled by exchanging heat with the first evaporator. At this time, since the cooled air has a relative humidity as high as about 80 to 100% RH, the adsorbent easily adsorbs moisture (the relative humidity difference between the air and the adsorbent increases). The cooled introduced air flows into the adsorption side area of the moisture adsorption means 20, and moisture is adsorbed and dehumidified by the adsorbent. Further, the dehumidified introduced air is cooled by exchanging heat with the fourth heat exchanger 5d (third evaporator) to be supplied as indoor introduced air SA. On the other hand, in the exhaust discharge path B, the introduced air introduced from the room air RA is humidified by the total heat exchanger 10 and then sent to the first heat exchanger 5a (condenser). Here, the introduced air is heated by exchanging heat with the condenser. At this time, since the heated air has a relative humidity as low as about 5 to 25% RH, the adsorbent easily desorbs (releases) moisture (the relative humidity difference between the air and the adsorbent increases). The heated introduced air flows into the regeneration side region of the moisture adsorbing means 20, and moisture is desorbed and humidified by the adsorbent. The humidified introduced air is cooled by exchanging heat with the third heat exchanger 5c (second evaporator), becomes exhaust EA, and is discharged outside the room. At this time, the third heat exchanger 5c collects exhaust heat from the high-temperature exhaust gas, and raises the evaporating temperature on the refrigerant circuit side, thereby increasing the refrigeration cycle operation efficiency.

(Heating operation mode)
In the heating and humidifying operation (FIGS. 3 and 4), in the outside air introduction path A of the air conditioner, after the introduced air introduced from the outside air OA is humidified by the total heat exchanger 10, the second heat exchanger 5b ( Sent to the condenser). Here, the introduced air is heated by exchanging heat with the condenser. At this time, since the heated air has a relative humidity as low as about 5 to 25% RH, the adsorbent easily desorbs (releases) moisture (the relative humidity difference between the air and the adsorbent increases). The heated introduced air flows into the regeneration side region of the moisture adsorbing means 20, and moisture is desorbed and humidified by the adsorbent. The humidified introduced air is cooled by exchanging heat with the fourth heat exchanger 5d (second evaporator), becomes indoor introduced air SA, and is supplied indoors. At this time, the fourth heat exchanger 5d recovers heat from high-temperature air, and raises the evaporating temperature on the refrigerant circuit side, thereby improving the refrigeration cycle operation efficiency. Further, the heating effect (sensible heat heating) can be obtained by controlling the amount of heat exchange in the fourth heat exchanger 5d so that the SA after recovering the heat is higher than the indoor set temperature. It is possible to obtain both the SA heating effect and the humidification increase effect by heat recovery. On the other hand, in the exhaust discharge path B, the introduced air introduced from the room air RA is dehumidified by the total heat exchanger 10 and then sent to the first heat exchanger 5a (first evaporator). Here, the introduced air is cooled by exchanging heat with the first evaporator. At this time, since the cooled air has a relative humidity as high as about 80 to 100% RH, the adsorbent easily adsorbs moisture (the relative humidity difference between the air and the adsorbent increases). The cooled introduced air flows into the adsorption side area of the moisture adsorption means 20, and moisture is adsorbed and dehumidified by the adsorbent. Furthermore, the dehumidified introduced air is cooled by exchanging heat with the third heat exchanger 5c (third evaporator), becomes exhaust EA, and is discharged outside the room.

  FIG. 5 is an example of the adsorption characteristics of the adsorbent carried on the moisture adsorption means 20. When the relative humidity [%] is taken on the horizontal axis and the water vapor adsorption amount [wt%] is taken on the vertical axis, the water vapor adsorption amount suddenly increases and rises at a certain relative humidity as shown in FIG.

  By disposing a cooling evaporator (first evaporator) upstream of the adsorption side region of the moisture adsorbing means 20, the relative humidity of the introduced air serving as the adsorbed air of the moisture adsorbing means 20 is close to 80 to 100% RH. It can be raised. Further, by arranging a condenser for heating upstream of the regeneration side region of the moisture adsorbing means 20, it is possible to reduce the relative humidity of the introduced air that is the regeneration air of the moisture adsorbing means 20 to about 5 to 25% RH. It becomes. As a result, the relative humidity difference ΔRH between the adsorbed air and the regenerated air is increased, so that the adsorption / desorption capability Δq of the adsorbent in the moisture adsorption means 20 is increased, and a large dehumidifying / humidifying capability can be obtained. The above effects can be surely exerted more reliably when an adsorbent having a characteristic of rising rapidly with a relative humidity having a water vapor adsorption amount as shown in FIG. 5 is used.

<< Explanation of the effects of system operation >>
The system operation will be described with reference to the air diagrams of FIGS.
(Cooling and dehumidifying operation mode)
In (a) of FIG. 2, in the outside air introduction path A during the cooling and dehumidification of the air conditioner, the introduction air (state 1) introduced from the outside air OA is discharged from the room air RA in the total heat exchanger 10. After total heat exchange with air (state 6), as the known state change process of the total heat exchanger, the state changes along the straight line connecting state 1 and state 2, enthalpy decreases, temperature and absolute Humidity decreases (state 2). The enthalpy is reduced and the introduced air (state 2) dehumidified and cooled is sent to the second heat exchanger 5b (first evaporator), and the relative humidity increases by being cooled (state 3). The introduced air with increased relative humidity (state 3) flows into the adsorption region of the moisture adsorbing means 20, moisture is adsorbed in the isoenthalpy process, and the absolute humidity decreases (state 4). Since the temperature of the introduced air (state 4) whose absolute humidity has decreased is increased by the heat of adsorption of the desiccant (adsorbent), it is sent to the fourth heat exchanger 5d (third evaporator) and cooled again ( State 5). This cooled introduction air (state 5) is supplied to the indoor space as the indoor introduction air SA.

  As described above, in the air conditioner, by introducing the fourth heat exchanger 5d (third evaporator) downstream of the adsorption side region of the moisture adsorbing means 20, the introduced air particularly during the cooling operation. It is possible to remove the sensible heat due to the temperature rise due to the heat of adsorption of the adsorbent at, thereby reducing the cooling load. Moreover, the effect of improving the efficiency of the refrigeration cycle (refrigerant circuit side) can be obtained by collecting the adsorption heat of the adsorbent.

  The introduced air SA (state 5) obtained in this way can be dehumidified by the desiccant (adsorbent), in addition to dehumidification by the total heat exchanger 10, and therefore by total heat exchange. As in the case of adsorption dehumidification by dehumidification + desiccant, the absolute humidity is greatly reduced by the double dehumidification effect, and a high dehumidification effect can be obtained.

  In FIG. 2B, in the exhaust discharge path B, exhaust air introduced from the room air RA (state 6) is totally exchanged with the introduced air introduced from the outside air OA (state 1) in the total heat exchanger 10. As a result, enthalpy increases, temperature rises, and absolute humidity increases (state 7). The enthalpy increases and the humidified and heated air (state 7) is sent to the first heat exchanger 5a (condenser) to be heated by heat exchange, and the relative humidity decreases (state 8). The exhausted air (state 8) having a decreased relative humidity flows into the regeneration region of the moisture adsorbing means 20, and moisture is desorbed in the isoenthalpy process, thereby increasing the relative humidity (state 9). The exhausted air (state 9) having an increased relative humidity is sent to the third heat exchanger 5c (second evaporator) installed downstream of the regeneration region of the moisture adsorption means 20, and the temperature is increased by heat exchange. It decreases and is discharged to the outside as exhaust EA (state 10).

  Further, in the exhaust discharge path B, the exhaust heat of the condenser is used for regeneration of the desiccant, and the regeneration exhaust heat, which is the high-temperature air after regeneration, is introduced into the second evaporator to recover the exhaust heat. The input of the compressor 1 in the refrigerant circuit can be reduced, an energy saving effect can be obtained, and the efficiency of the system can be improved.

(Heating and humidifying operation mode)
In (a) of FIG. 4, in the outside air introduction path A at the time of cooling and dehumidification of the air conditioner, the introduction air introduced from the outside air OA (state 1) is discharged from the room air RA in the total heat exchanger 10. After total heat exchange with air (state 6), the state changes along the straight line connecting state 1 and state 2 as the known state change process of the total heat exchanger, enthalpy increases and temperature rises Absolute humidity increases (state 2). The enthalpy increases and the humidified and heated air (state 2) is sent to the second heat exchanger 5b (condenser) where it is heat-exchanged and heated, and the relative humidity decreases (state 3). The exhausted air (state 3) having a decreased relative humidity flows into the regeneration region of the moisture adsorbing means 20, is desorbed with moisture in the isoenthalpy process, and the relative humidity increases (state 4). The exhausted air (state 4) having an increased relative humidity is sent to a fourth heat exchanger 5d (second evaporator) installed downstream of the regeneration region of the moisture adsorption means 20, and the temperature is increased by heat exchange. It decreases (state 5) and is supplied to the indoor space as the indoor introduction air SA.

  The introduced air SA (state 5) thus obtained can be humidified by the desiccant (adsorbent) in addition to the humidification by the total heat exchanger 10, so that the humidification by the total heat exchange + the desorption humidification by the desiccant Thus, the absolute humidity increases due to the double humidification effect, and a high humidification effect can be obtained. In addition, moisture in the air is adsorbed by a total heat exchanger or desiccant, and is released to the introduced air SA side to humidify the air, so that it is possible to perform humidification without supplying water and eliminate the need for water pipe work. .

  In addition, the exhaust heat of the condenser is used for regeneration of the desiccant, and regeneration heat, which is high-temperature air after regeneration, is introduced into the second evaporator for heat recovery, so that the input of the compressor 1 in the refrigerant circuit is performed. Can be reduced, energy saving effect can be obtained, leading to higher efficiency in the system.

  4B, in the exhaust discharge path B, the exhaust air introduced from the room air RA (state 6) is totally exchanged with the introduced air introduced from the outside air OA (state 1) in the total heat exchanger 10. As a result, the enthalpy decreases, and the temperature and absolute humidity decrease (state 7). The enthalpy is reduced and the introduced air (state 7) dehumidified and cooled is sent to the first heat exchanger 5a (first evaporator), and the relative humidity increases by being cooled (state 8). The introduced air with increased relative humidity (state 8) flows into the adsorption region of the moisture adsorption means 20, and moisture is adsorbed in the isoenthalpy process, and the absolute humidity is reduced (state 9). Since the temperature of the introduced air (state 9) in which the absolute humidity has decreased is increased by the heat of adsorption of the desiccant (adsorbent), it is sent to the third heat exchanger 5d (third evaporator) and cooled again ( State 10). This cooled exhaust air (state 10) is exhausted to the outside as exhaust EA (state 10).

  As described above, the efficiency of the refrigeration cycle (refrigerant circuit side) is improved by recovering the adsorption heat of the adsorbent of the moisture adsorbing means 20 in the exhaust discharge path B to the fourth heat exchanger (third evaporator). The effect of can be obtained.

<System control method>
The sensors necessary for the control described in FIGS. 1 and 3 will be described. In the air conditioner of the present invention, on the refrigerant circuit side, a temperature sensor 6a for detecting the pipe temperature of the first heat exchanger, a temperature sensor 6b for detecting the pipe temperature of the second heat exchanger, and a third heat A temperature sensor 6c for detecting the pipe temperature of the exchanger, a temperature sensor 6d for detecting the pipe temperature of the fourth heat exchanger, and a temperature sensor 6e for detecting the discharge temperature are provided on the discharge side of the compressor 1. On the air circuit side, the outlet air temperature and humidity of the first heat exchanger (relative humidity or absolute humidity, or dew point may be used. Hereinafter, the description of humidity of the temperature / humidity sensor indicates the same meaning). Temperature / humidity sensor 7a, temperature / humidity sensor 7b for detecting the outlet air temperature and humidity of the second heat exchanger, temperature / humidity sensor 7c for detecting the outlet air temperature and humidity of the third heat exchanger, and fourth heat A temperature / humidity sensor 7d for detecting the outlet air temperature and humidity of the exchanger, a temperature / humidity sensor 7e for detecting the air temperature and humidity of the outside air OA, and a temperature / humidity sensor 7f for detecting the air temperature and humidity of the indoor air RA are provided. Yes. These temperature and humidity sensors are connected to a control board (not shown) that controls the air conditioner. The control board obtains the temperature and humidity information, and controls the compressor 1, the expansion valves 3a, b, c, the outside air introduction path A, and the exhaust discharge path B that are control actuators. Control can be performed.

  In the refrigerant circuit configuration of the present invention, expansion valves 3a to 3c for controlling the flow rate are provided for the first to third evaporators, respectively. Therefore, since the cooling capacity of each evaporator can be controlled by controlling the amount of refrigerant circulation based on the temperature of each evaporator or the air temperature and humidity at the outlet of each evaporator, until just before the passing air is saturated in each evaporator. It is possible to eliminate the drain treatment by cooling and preventing condensation. Condensation is prevented by setting the refrigerant temperature of each evaporator above the dew point temperature, but this dew point temperature can be obtained by measuring the temperature and humidity, so measure the tube temperature of each evaporator and the dew point temperature at that time The above control may be performed.

  FIG. 6 shows an example of an air conditioning system in which the air conditioning apparatus 100 of this embodiment and the sensible heat treatment apparatus 200 are combined. An air conditioner according to the present invention is arranged behind the ceiling of the air-conditioning target room, and a suction port for the wind EA that sucks the indoor air RA, which is the air path, and blows the air outside the room, and a blowout port that blows the blown air SA to the room of the outdoor air OA. Located on the ceiling. Further, a sensible heat treatment apparatus 200, which is an air conditioner different from this, is similarly attached to the ceiling, and blows out air into the room by blowing out air from the room and processing the sensible heat load in the room. In this system configuration, the air conditioning apparatus 100 of the present invention is used as an air conditioning outside air processing air conditioning apparatus that introduces outside air and exhausts indoor air to the outside, and mainly performs humidity adjustment when introducing outside air into the room. (Latent heat treatment) In addition to this, an air conditioner for sensible heat treatment is provided with another refrigerant circuit. As a result, the air conditioning apparatus 200 for sensible heat treatment does not need to be dehumidified, so that the operation of increasing the evaporation temperature of the refrigerant is possible, and the compressor can be operated with high efficiency with a low differential pressure. Therefore, in such a system configuration in which the outside air treatment air conditioner and the sensible heat treatment air conditioner are separately provided, the sensible heat load occupying a large proportion of the air conditioning load is covered by the sensible heat treatment air conditioner capable of high-efficiency operation. It becomes possible to increase the efficiency of the entire air conditioning system. The sensible heat treatment apparatus 200 includes a heat exchanger that cools indoor air and a blower that blows air in a main body provided on the ceiling, and a heat source unit of a heat pump unit that processes the heat of the heat exchanger. Are arranged outdoors and connected by piping. However, this sensible heat treatment apparatus may be a wall-mounted type or a floor-standing type, or may be a structure integrated with a heat source machine instead of a separate type. The air conditioning apparatus 100 and the sensible heat treatment apparatus 200 set a target temperature and a target humidity with a remote controller or the like, and control the refrigerant flowing through the refrigerant circuit with a throttling device or the like so as to obtain the target value. At this time, the compressor is operated so as to obtain high efficiency.

  When performing the refrigeration cycle operation, a large amount of refrigerant exists in a condenser through which a high-pressure gas refrigerant having a high density and a liquid refrigerant (high density) obtained by liquefying and condensing the refrigerant are flowing. For this reason, the amount of refrigerant contained in the refrigeration cycle greatly depends on the size of the condenser. In the present embodiment, the circuit configuration is such that the first heat exchanger 5a is a condenser during cooling and the second heat exchanger 5b is a condenser during heating, and the first heat exchanger 5a and the second heat exchange. The internal volume of the vessel 5b is approximately equal. Therefore, the amount of refrigerant required during the cooling operation and the heating operation can be made substantially equal, so that it is possible to configure without adding parts such as a liquid reservoir to the refrigeration cycle. As a result, the number of circuit components can be reduced and simplified, and the apparatus can be reduced in size and cost.

  In the air conditioner shown in FIGS. 1 and 3, the first heat exchanger 5a and the second heat exchanger 5b having a large internal volume and substantially the same capacity have the same thickness, and the internal volume is small and the capacity is small. It is possible to make the third heat exchanger 5c and the fourth heat exchanger 5d having substantially the same thickness substantially the same. Further, the third heat exchanger 5c and the fourth heat exchanger 5d can be thin because they may have a small capacity. By designing the thickness of each heat exchanger in this way and arranging and configuring the first to fourth heat exchangers 5a to 5d and the moisture adsorbing means 20 in the order shown in FIGS. It becomes possible to store the components of the part constituted by the containers 5a to 5d and the moisture adsorbing means 20 without wasting space, and to reduce the total thickness. Such a configuration is possible because of a device configuration in which air flows in parallel to the moisture adsorbing means 20.

  Further, the heat exchangers 5a to 5d and the moisture adsorbing means 20 are installed in the horizontal direction, and the order of installation in the vertical direction is the third heat exchanger 5c, the fourth heat exchanger 5d, and the middle part. In the order of the moisture adsorbing means 20 at the bottom and the first heat exchanger 5c and the second heat exchanger 5d at the bottom, the air flow is directed upward from below vertically with respect to the heat exchangers 5a to 5d and the moisture adsorbing means 20. (A configuration in which FIGS. 1 and 3 are reversed in the vertical direction). Thereby, it becomes the flow which air blows up perpendicularly upwards with respect to the heat exchangers 5a-5d. Therefore, in the case where the heat exchangers 5a to 5d are evaporators, even when the heat exchanger is slightly condensed, the airflow flows upward, so that it is difficult for water droplets to drip. Further, if the wind speed is increased, water droplets can be blown off, and the generation of drain water can be suppressed.

Embodiment 2. FIG.
"System configuration"
7 to 9 illustrate an air-conditioning apparatus according to Embodiment 2 of the present invention. FIG. 7 is a configuration diagram schematically showing an air path configuration in the cooling / dehumidifying operation mode, FIG. 8 is a configuration diagram schematically showing an air path configuration in the heating / humidifying operation mode, and FIG. 9 is a refrigeration cycle operation in the refrigerant circuit configuration. It is a Ph diagram showing the operation of. In addition, the same code | symbol is attached | subjected about the part same as Embodiment 1, or an equivalent part, and description is abbreviate | omitted. In addition, this embodiment is characterized by the refrigerant circuit side, and the operating state (cooling dehumidification operation, heating / humidification operation) on the humid air diagram on the air circuit side is basically the same as that of the first embodiment. The diagram and the explanation regarding this will be omitted.

  7 and 8, the air conditioner includes a compressor 1, four-way valves 2a and 2b, expansion valves 3a, 3d and 3e, check valves 4a and 4b, a first heat exchanger 5a and a second heat exchange. A refrigerant circuit composed of a heat exchanger 5b, a third heat exchanger 5c, and a fourth heat exchanger 5d, a total heat exchanger 10, and a moisture adsorption means 20 that repeats adsorption and release (regeneration) of moisture. is doing.

  The first heat exchanger 5a is connected in series with the second heat exchanger 5b via the expansion valve 3a, and the first heat exchanger 5a is a condenser and a second heat exchanger during the cooling and dehumidifying operation. 5b operates as a first evaporator (FIG. 7), and is configured so that the second heat exchanger 5b operates as a condenser and the first heat exchanger 5a operates as a first evaporator during the heating and humidifying operation. (FIG. 8).

The check valves 4a and 4b have an inlet side of the check valve 4a between the first heat exchanger 5a and the expansion valve 3a, and an inlet of the check valve 4b between the second heat exchanger 5b and the expansion valve 3a. A side is provided. And after each outlet side merges once, it is connected to the expansion valve 3e. A four-way valve 2b is connected downstream of the expansion valve 3e. In the four-way valve 2b, the circuit configuration of the third heat exchanger 5c, the expansion valve 3d, the fourth heat exchanger 5d, the four-way valve 2b, and the suction side of the compressor 1 in this order during the cooling and dehumidifying operation (FIG. 7). In the heating and humidifying operation, the circuit is configured so that the fourth heat exchanger 5d, the expansion valve 3d, the third heat exchanger 5c, the four-way valve 2b, and the suction side of the compressor 1 are configured in this order (FIG. 8). Built in to work. The third heat exchanger 5c operates as the second evaporator and the fourth heat exchanger 5d operates as the third evaporator during the cooling and dehumidifying operation, and the third heat exchanger 5c operates as the third evaporator during the heating and humidifying operation. The evaporator and the fourth heat exchanger 5d operate as the second evaporator. In the present example, as in the first embodiment, the role of the three evaporators that change roles between the cooling and dehumidifying operation and the heating and humidifying operation is the same as that of the moisture adsorbing unit 20 in each operation mode. Is defined as the first evaporator, the evaporator located on the regeneration side leeward is defined as the second evaporator, and the evaporator located on the adsorption side leeward is defined as the third evaporator.
<Operation description of refrigerant circuit>

Next, the operation switching operation between the cooling / dehumidifying operation and the heating / humidifying operation of the refrigerant circuit will be described.
Switching between the cooling and dehumidifying operation and the heating and humidifying operation is performed by switching the four-way valves 2a and 2b and by operating the check valves 4a and 4b.

(Cooling and dehumidifying operation mode)
In the cooling and dehumidifying operation (FIG. 7), the four-way valve 2a is set to be connected to the discharge side of the compressor 1 and the first heat exchanger 5a. The first heat exchanger 5a operates as a condenser, and the refrigerant that has passed through the expansion valve 3a is decompressed to a low temperature and a low pressure and then flows into the second heat exchanger. Here, the second heat exchanger 5b operates as a first evaporator. At this time, since a large differential pressure is generated before and after the expansion valve 3a, the differential pressure acts on the check valve 4b in the reverse direction to be “closed”, and a differential pressure is generated in the check valve 4a in the forward direction. Open ". Then, the high-temperature and high-pressure refrigerant that has passed through the check valve 4a passes through the expansion valve 3e, becomes intermediate temperature and intermediate pressure, and flows into the third heat exchanger 5c through the four-way valve 2b. The third heat exchanger 5c operates as a second evaporator, and the refrigerant becomes low-temperature and low-pressure through the expansion valve 3d and flows into the fourth heat exchanger 5d. The fourth heat exchanger 5d operates as a third evaporator, and the refrigerant returns to the suction side of the compressor 1. Similarly, the refrigerant that has passed through the second heat exchanger 5b also returns to the suction side of the compressor 1.

(Heating and humidifying operation mode)
In the heating and humidifying operation (FIG. 8), the four-way valve 2a is set to be connected to the discharge side of the compressor 1 and the second heat exchanger 5b. The second heat exchanger 5b operates as a condenser, and the refrigerant having passed through the expansion valve 3a is depressurized to a low temperature and a low pressure and then flows into the first heat exchanger 5a. Here, the first heat exchanger 5a operates as a first evaporator. At this time, since a large differential pressure is generated before and after the expansion valve 3a, the differential pressure acts in the reverse direction on the check valve 4a to be “closed”, and the differential pressure is generated in the forward direction on the check valve 4b. Open ". Then, the high-temperature and high-pressure refrigerant that has passed through the check valve 4b becomes an intermediate-temperature / intermediate pressure through the expansion valve 3e, and flows into the fourth heat exchanger 5d through the four-way valve 2b. The fourth heat exchanger 5d operates as a second evaporator, and the refrigerant becomes low-temperature and low-pressure through the expansion valve 3d and flows into the third heat exchanger 5c. The third heat exchanger 5 c operates as a third evaporator, and the refrigerant returns to the suction side of the compressor 1. Similarly, the refrigerant that has passed through the first heat exchanger 5a also returns to the suction side of the compressor 1.

(Operation on refrigeration cycle)
FIG. 9 shows the operation on the refrigeration cycle in the cooling / dehumidifying operation or the heating / humidifying operation described above on the Ph diagram. In this embodiment, the low pressure side of the refrigeration cycle constituted by the refrigerant circuit is a parallel circuit of two systems, and further, one system includes an expansion valve 3e, a second evaporator, an expansion valve 3d, and a third circuit. The evaporator is connected in two stages in series. Therefore, in the system on the side where the second evaporator and the third evaporator are connected, the second evaporation connected downstream of the expansion valve 3e by changing the opening ratio of the expansion valves 3e and 3d. It becomes possible to adjust the refrigerant pressure (intermediate pressure) of the vessel. As a result, the second evaporator and the third evaporator can be operated at different evaporation temperatures (evaporation temperature of the second evaporator> evaporation temperature of the third evaporator).

  On the upstream side of the air circuit of the second evaporator, the regeneration side of the moisture adsorbing means 20 is arranged. For this reason, the inlet air of the second evaporator is in a state of higher humidity than the other evaporators (first and third). As described above, the second evaporator and the third evaporator have a two-stage configuration in series, so that it is possible to operate by increasing the refrigerant temperature of the second evaporator where condensation easily occurs. For example, by controlling the piping temperature (temperature sensor 5c or 5d) of the second evaporator to a dew point or higher, it is possible to reliably prevent condensation in the second evaporator. As a result, the drain pan can be eliminated from the air conditioner, and the device configuration can be simplified. In addition, by operating the second evaporator and the third evaporator optimally at different evaporation temperatures, a practical device with convenient operation switching that can increase the efficiency of the refrigeration cycle is obtained.

Embodiment 3 FIG.
"System configuration"
10 and 11 illustrate an air-conditioning apparatus according to Embodiment 3 of the present invention. FIG. 10 is a configuration diagram schematically showing an air path configuration in the cooling and dehumidifying operation mode, and FIG. 11 is a configuration diagram schematically showing an air path configuration in the heating and humidifying operation mode. In addition, the same code | symbol is attached | subjected about the same part as Embodiment 1, 2, or a corresponding part, and description is abbreviate | omitted. The refrigerant circuit of the present example is a circuit equivalent to the second embodiment although the configuration is different, and the effect is the same as that of the second embodiment. In addition, since the operation state (cooling dehumidifying operation and heating / humidifying operation) on the humid air diagram on the air circuit side is basically the same as in the first and second embodiments, the air diagram and the explanation related thereto are omitted. .

  10 and 11, the air conditioner includes a compressor 1, a four-way valve 2a, expansion valves 3a, 3d, 3f, and 3g, a first heat exchanger 5a, a second heat exchanger 5b, and a third heat. A refrigerant circuit composed of an exchanger 5c, a fourth heat exchanger 5d, and electromagnetic valves 8a and 8b, a total heat exchanger 10, and a moisture adsorption means 20 that repeats adsorption and release (regeneration) of moisture. ing.

  The first heat exchanger 5a is connected in series with the second heat exchanger 5b via the expansion valve 3a, and the first heat exchanger 5a is a condenser and a second heat exchanger during the cooling and dehumidifying operation. 5b operates as a first evaporator (FIG. 10), and is configured so that the second heat exchanger 5b operates as a condenser and the first heat exchanger 5a operates as a first evaporator during the heating and humidifying operation. (FIG. 11).

The expansion valves 3f and 3g are provided with an inlet side of the expansion valve 3f between the first heat exchanger 5a and the expansion valve 3a, and an inlet side of the expansion valve 3g between the second heat exchanger 5b and the expansion valve 3a. ing. And
The outlet side of the expansion valve 3f is connected to the third heat exchanger 5c, and the outlet side of the expansion valve 3g is connected to the fourth heat exchanger 5d. During the cooling and dehumidifying operation, the third heat exchanger 5c, the expansion valve 3d, the fourth heat exchanger 5d, the electromagnetic valve 8b (open), and the suction side of the compressor 1 are configured in this order (FIG. 10). During operation, the fourth heat exchanger 5d, the expansion valve 3d, the third heat exchanger 5c, the electromagnetic valve 8a (open), and the suction side of the compressor 1 are configured in this order (FIG. 11). The third heat exchanger 5c operates as the second evaporator and the fourth heat exchanger 5d operates as the third evaporator during the cooling and dehumidifying operation, and the third heat exchanger 5c operates as the third evaporator during the heating and humidifying operation. The evaporator and the fourth heat exchanger 5d operate as the second evaporator. In this example, as in the first and second embodiments, the role of the three evaporators that change roles in the cooling and dehumidifying operation and the heating and humidifying operation is adsorbed to the moisture adsorbing means 20 in each operation mode. The evaporator located on the side wind is defined as the first evaporator, the evaporator located on the regeneration side lee is defined as the second evaporator, and the evaporator located on the adsorption side lee is defined as the third evaporator.
<Operation description of refrigerant circuit>

Next, the operation switching operation between the cooling / dehumidifying operation and the heating / humidifying operation of the refrigerant circuit will be described.
Switching between the cooling and dehumidifying operation and the heating and humidifying operation is performed by opening the expansion valves 3f and 3g and opening and closing operations of the electromagnetic valves 8a and 8b.

(Cooling and dehumidifying operation mode)
In the cooling and dehumidifying operation (FIG. 10), the four-way valve 2a is set so that the discharge side of the compressor 1 and the first heat exchanger 5a are connected. The first heat exchanger 5a operates as a condenser, and the refrigerant that has passed through the expansion valve 3a is depressurized to a low temperature and a low pressure and then flows into the second heat exchanger 5b. Here, the second heat exchanger 5b operates as a first evaporator. In addition, the refrigerant passes through the expansion valve 3f, becomes intermediate temperature and intermediate pressure, and flows into the third heat exchanger 5c. The third heat exchanger 5c operates as a second evaporator, and the refrigerant becomes low-temperature and low-pressure through the expansion valve 3d and flows into the fourth heat exchanger 5d. The fourth heat exchanger 5d operates as a third evaporator, and the refrigerant returns to the suction side of the compressor 1 through the electromagnetic valve 8b (open). Similarly, the refrigerant that has passed through the second heat exchanger 5b also returns to the suction side of the compressor 1. Here, the expansion valve 3g is fully closed, and the electromagnetic valve 3a is closed. Since the refrigerant does not flow through the pipes passing through them, the circuit described above is established.

(Heating and humidifying operation mode)
In the heating and humidifying operation (FIG. 11), the four-way valve 2a is set to be connected to the discharge side of the compressor 1 and the second heat exchanger 5b. The second heat exchanger 5b operates as a condenser, and the refrigerant having passed through the expansion valve 3a is depressurized to a low temperature and a low pressure and then flows into the first heat exchanger 5a. Here, the first heat exchanger 5a operates as a first evaporator. In addition, the refrigerant passes through the expansion valve 3g, becomes an intermediate temperature / intermediate pressure, and flows into the fourth heat exchanger 5d. The fourth heat exchanger 5d operates as a second evaporator, and the refrigerant becomes low-temperature and low-pressure through the expansion valve 3d and flows into the third heat exchanger 5c. The third heat exchanger 5c operates as a third evaporator, and the refrigerant returns to the suction side of the compressor 1 through the electromagnetic valve 8a (open). Similarly, the refrigerant that has passed through the second heat exchanger 5b also returns to the suction side of the compressor 1. Here, the expansion valve 3f is fully closed, the electromagnetic valve 3b is closed, and the refrigerant does not flow through the piping passing through them, so the circuit described above is established.

(Operation on refrigeration cycle)
In the refrigerant circuit configuration of this example, similarly to the second embodiment, the second evaporator and the third evaporator can be operated in two stages connected in series. Therefore, the same effect as in the second embodiment, that is, the second evaporator and the third evaporator can be operated at different evaporation temperatures (evaporation temperature of the second evaporator> third evaporation). It is possible to reliably prevent condensation in the second evaporator. As a result, the drain pan can be eliminated from the air conditioner, and the device configuration can be simplified. In addition, it is possible to increase the efficiency of the refrigeration cycle by optimally operating the second evaporator and the third evaporator at different evaporation temperatures. 10 and 11, the electromagnetic valves 8a and 8b are used instead of the four-way valve 2b used in FIG. 7 and the like, so that even a small pressure difference can be reliably closed, and an efficient and practical device is possible.

  1, 3, 7, 8, 10, and 11, the outside air introduction path A and the outside air introduction path with respect to the moisture adsorbing means are shown in the drawings. Although the wind flow of B is made into the same direction (parallel flow), it is not limited to this, It is good also as a counterflow which makes the wind flow of the external air introduction path | route A and the external air introduction path | route B reverse.

  The present invention is not only provided with a condenser on the suction air passage side on the regeneration side of the desiccant but also provided with an evaporator on the blow-off side, and further provided with an evaporator on the blow-off air passage side on the adsorption side of the desiccant and also evaporated on the suction side. It is possible to control the temperature closer to the indoor target temperature, improve the efficiency of the refrigerant circuit by using regenerative exhaust heat, and adjust the cooling capacity of each evaporator so that it does not condense. The relative humidity difference between adsorption and regeneration is increased by the first evaporator and the condenser on the regeneration side, thereby increasing the dehumidification and humidification performance. In addition, since the above effect is realized only by switching the refrigerant circuit side, not the air side circuit, in the switching operation between the cooling and dehumidifying operation and the heating and humidifying operation, a damper that increases the size of the device is unnecessary, and Miniaturization and simplification are possible.

  In addition, it is possible to control the refrigerant flow rate and the refrigerant temperature by individually providing an expansion valve corresponding to each evaporator, in addition to preventing condensation of the evaporator during cooling and dehumidifying operation, and preventing condensation during heating and humidifying operation, The effect of preventing frost formation is obtained.

The air conditioner of the present invention forms a first air flow path that forms a flow of air from the first space toward the second space, and a flow of air that flows from the second space toward the first space. A second air flow path, a total heat exchanger that performs total heat exchange between air flowing through the first air flow path and air flowing through the second air flow path, a compressor that compresses the refrigerant, A refrigerant circuit including a valve, a throttle device, a first heat exchanger, a second heat exchanger, a third heat exchanger, and a fourth heat exchanger, a first air flow path, and a second Arranged across the air flow path, adsorbs and dehumidifies in one of the first and second air flow paths, and the area is moved to the other air flow path for heat regeneration. And a moisture adsorbing means that repeats the operation alternately. The refrigerant circuit includes a first heat exchanger as a condenser, a second heat exchanger as a first evaporator, and a third heat exchanger. A first refrigerant circuit configuration using the exchanger as the second evaporator and the fourth heat exchanger as the third evaporator, and the first heat exchanger as the first evaporator and the second heat exchanger Can be switched to the second refrigerant circuit configuration using the first refrigerant as the condenser, the third heat exchanger as the third evaporator, and the fourth heat exchanger as the second evaporator. When the circuit configuration is used, the total heat exchanger, the condenser, the moisture adsorbing means, and the second evaporator are sequentially configured from the windward side to the leeward side in the first air flow path, When the first evaporator, the moisture adsorbing means, and the third evaporator are sequentially configured from the windward side to the leeward side in the air flow path, and the second refrigerant circuit configuration is used, the first air flow path In addition, the total heat exchanger, the first evaporator, the moisture adsorption means, and the third evaporator are sequentially configured from the leeward side to the leeward side, Since the condenser, the moisture adsorbing means, and the second evaporator are sequentially configured in the air flow path 2 from the windward side to the leeward side, the latent heat in the air-conditioning target space can be efficiently processed, Sensible heat treatment is also possible.

  Since the expansion device of the present invention is composed of a plurality, and each expansion device is provided corresponding to the upstream side of the first to third evaporators, each evaporator can be set to a dew point temperature or higher. it can. Each throttle device may be an adjustment valve whose opening degree can be adjusted, or a device that sets a fixed value, such as a capillary tube, so that the refrigerant temperature of each evaporator is ensured to be almost a predetermined value or more. Also good.

  In the air conditioner of the present invention, the second evaporator and the third evaporator provided in parallel with the first evaporator can be connected in series or in parallel in this order. Is possible.

  The rate of change of the equilibrium adsorption amount of moisture relative to the relative humidity of the adsorbent provided in all or part of the moisture adsorbing means of the present invention is a first relative humidity and a humidity higher than the first relative humidity. In the range between the relative humidity of 2 and the higher relative humidity than the first relative humidity and higher than the second relative humidity, moisture adsorption and desorption Can be done effectively. In this case, it is preferable that the first relative humidity is about 30% and the second relative humidity is about 60%.

  In addition, if the moisture adsorbing means is provided with a solid adsorbing material, and the solid adsorbing material is composed of a silicon material provided with a large number of pores having a hole diameter of 1.5 to 2.5 nanometers, moisture adsorption and desorption can be achieved. Done effectively.

  In the air conditioner according to the present invention, the refrigerant circulation amount or the refrigerant temperature can be controlled so that the refrigerant evaporation temperature in each evaporator does not fall below the dew point of the intake air temperature of the evaporator. Therefore, the entire apparatus can be simplified.

  The first space of the present invention is an air-conditioning chamber, the second space is an outdoor space, and the air-conditioning chamber is air-cooled and dehumidified (first refrigerant circuit configuration) or heated and humidified (second refrigerant circuit configuration). be able to. Further, by using the air conditioner of the present invention as an outside air treatment air conditioner and providing an air conditioner for sensible heat treatment, a more efficient air conditioner system can be obtained.

  This invention makes the internal volume of the heat exchanger which becomes a condenser at the time of cooling operation and the heat exchanger which becomes a condenser at the time of heating operation substantially the same. Moreover, it is set as the structure which the flow of air flows upwards from perpendicular | vertical downward with respect to either of several heat exchangers.

The circuit block diagram at the time of the air_conditioning | cooling dehumidification driving | operation of the air conditioning apparatus which concerns on Embodiment 1 of this invention. The humid air line figure which shows the operation state in the air_conditioning | cooling dehumidification driving | operation shown in FIG. 1 of this invention. The circuit block diagram at the time of the heating humidification operation | movement of the air conditioning apparatus which concerns on Embodiment 1 of this invention. The humid air line figure which shows the operation state in the heating humidification driving | operation shown in FIG. 1 of this invention. The figure which shows an example of the adsorption | suction characteristic of the adsorbent in the air conditioning apparatus shown to FIG. The figure of the example of air-conditioning system composition concerning Embodiment 1 of the present invention. The circuit block diagram at the time of the air_conditioning | cooling dehumidification operation | movement of the air conditioning apparatus which concerns on Embodiment 2 of this invention. The circuit block diagram at the time of the heating humidification operation | movement of the air conditioning apparatus which concerns on Embodiment 2 of this invention. The ph diagram which showed the refrigerant circuit operation state in the air conditioning apparatus shown to FIG. 8, 9 of this invention. The circuit block diagram at the time of the air_conditioning | cooling dehumidification driving | operation of the air conditioning apparatus which concerns on Embodiment 3 of this invention. The circuit block diagram at the time of the heating humidification operation | movement of the air conditioning apparatus which concerns on Embodiment 3 of this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 Compressor, 2a, b Four-way valve, 3a, b, c, d, f, g Expansion valve, 4a, b Check valve, 5a 1st heat exchanger, 5b 2nd heat exchanger, 5c 3rd Heat exchanger, 5d Fourth heat exchanger, 6a, b, c, d, e Temperature sensor, 7a, b, c, d, e, f Temperature / humidity sensor, 8a, 8b Solenoid valve, 10 Total heat exchange 20: moisture adsorbing means, 100 air conditioning apparatus, 200 sensible heat treatment apparatus, A: outside air introduction path, B: exhaust discharge path, OA: outside air, RA: room air, SA: room introduction air.

Claims (12)

A first air flow path that forms a flow of air from the outdoor to the indoor;
A second air flow path that forms a flow of air from the room toward the outside of the room;
Adsorption dehumidification is arranged across the first air flow path and the second air flow path, and is located in one of the first air flow path and the second air flow path. A moisture adsorbing means that is regenerated by heating when it is located at the other and alternately repeats the adsorption dehumidification and the heating regeneration operations performed in the first air flow path and the second air flow path. ,
A plurality of heat exchangers arranged on the upstream side and the downstream side of each of the moisture adsorbing means disposed in the air flow of the first air channel and the second air channel;
In the compressor, the refrigerant is circulated through the plurality of heat exchangers, and is arranged on the upstream side of the air flow of both the moisture adsorbing means provided in the first air channel and the second air channel. A refrigerant circuit having a throttling device and a four-way valve that switches the flow of the refrigerant so that one of the heat exchangers is a condenser and the other is a first evaporator;
The heat flowing from the condenser to the first evaporator is disposed downstream of each of the moisture adsorbing means disposed in both the first air flow path and the second air flow path. A circuit branching to the exchanger, wherein the downstream side of the condenser is operated as a second evaporator and the downstream side of the first evaporator is operated as a third evaporator and returned to the compressor; An air conditioner comprising: A first air flow path that forms a flow of air from the first space toward the second space;
A second air flow path that forms an air flow from the second space toward the first space;
A total heat exchanger that performs total heat exchange between air flowing through the first air flow path and air flowing through the second air flow path;
A compressor that compresses the refrigerant, a four-way valve that switches the flow of the refrigerant, a throttling device that adjusts the flow of the refrigerant, and the air and the refrigerant that flow in the first air flow path and the second air flow path A refrigerant circuit in which a plurality of heat exchangers, which are a first heat exchanger, a second heat exchanger, a third heat exchanger, and a fourth heat exchanger, that exchange heat with each other are connected by piping;
The first air flow path and the second air flow path are disposed across the first air flow path and adsorbed and dehumidified in an area located on either one of the first or second air flow path. Moisture adsorption means that repeats the operation of moving to the other air flow path and regenerating by heating, and
The first heat exchanger is a condenser, the second heat exchanger is a first evaporator, the third heat exchanger is a second evaporator, and the fourth heat exchanger is a third In the case of the first refrigerant circuit as an evaporator,
In the first air flow path, the total heat exchanger, the condenser, the moisture adsorption means, and the second evaporator are sequentially arranged from the windward side to the leeward side,
In the second air flow path, the total heat exchanger, the first evaporator, the moisture adsorption means, and the third evaporator are sequentially arranged from the windward side to the leeward side. Refrigerant / wind circuit configuration,
The first heat exchanger is a first evaporator, the second heat exchanger is a condenser, the third heat exchanger is a third evaporator, and the fourth heat exchanger is a second evaporator. In the case of the second refrigerant circuit as an evaporator,
In the first air flow path, the total heat exchanger, the first evaporator, the moisture adsorbing means, and the third evaporator are sequentially arranged from the windward side to the leeward side,
In the second air flow path, the total heat exchanger, the condenser, the moisture adsorbing means, and the second evaporator are sequentially arranged from the windward side toward the leeward side. And an air conditioner that is switchable between the first refrigerant / wind circuit configuration and the second refrigerant / wind circuit configuration. The amount or temperature of the refrigerant is controlled so that the evaporation temperatures of the first evaporator, the second evaporator, and the third evaporator are equal to or higher than a dew point temperature. 2. The air conditioning apparatus according to 2. Both the first air flow path and the second air flow path are provided further upstream than the respective heat exchangers provided on the upstream side of the moisture adsorbing means; A total heat exchanger that performs total heat exchange with the second air flow path, and a throttling device that is provided in the refrigerant branch circuit and disposed upstream of each evaporator in the refrigerant flow. The air conditioning apparatus according to claim 1 or 2, wherein 4. The air conditioner according to claim 1, wherein the first evaporator, the second evaporator, and the third evaporator have different evaporation temperatures. 5. One of the heat exchangers provided in the first air flow path and the second air flow path and arranged on the upstream side of the air flow of both the moisture adsorbing means is a condenser and the other is a first evaporation. The air conditioner according to claim 1, 2 or 3, wherein the internal volumes of both of the heat exchangers used as a heat exchanger are substantially the same. 4. The air conditioner according to claim 1, wherein the internal volume of the second evaporator and the third evaporator is smaller than the internal volume of the first evaporator. 4. The air conditioner according to claim 1, wherein a plurality of pores having a hole diameter of nanometer are provided in at least a part of the moisture adsorbent provided on the surface of the moisture adsorbing means. apparatus. A plurality of the throttle devices, a return circuit for returning the refrigerant from the first throttle device to the compressor through the first evaporator, and the refrigerant from the second throttle device to the second evaporator. And a second return circuit that returns from the third throttling device through the third evaporator to the compressor in series or parallel is connected in parallel. The air conditioning apparatus described in 1. The first space is a room for air conditioning, the second space is an outdoor space, and the room is dehumidified with the first refrigerant / wind circuit configuration, or the second refrigerant / wind circuit configuration is provided. The air conditioner according to claim 2, wherein the room is heated and humidified. The air conditioner according to any one of claims 1 to 8, wherein any one of the plurality of heat exchangers is arranged to flow an air flow from vertically downward to upward. A sensible heat load in the room that performs air conditioning in the air conditioning apparatus according to claim 1 or 2 or 3 or 8 is processed by a second air conditioning apparatus having a refrigerant circuit provided separately. An air conditioning system characterized by

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