JP5311734B2 - Air conditioner - Google Patents

Description

  The present invention relates to an air conditioner that cools a chamber to be conditioned by air exchanged with an evaporator.

  Conventionally, this type of air conditioner has a refrigeration cycle including a compressor, a radiator, a decompressor, an evaporator, and the like. Then, the refrigerant compressed by the compressor is radiated by the radiator, depressurized by the decompressor, and then evaporated by the evaporator. At this time, the air (cold air) cooled by the evaporation of the refrigerant is conditioned chamber And air-conditioning (cooling) the conditioned room.

  By the way, in the apparatus provided with such a refrigerating cycle, the HFC refrigerant | coolant was generally used conventionally, However, Since the said HFC type | system | group refrigerant | coolant has a high warming potential, it tends to refrain from use in recent years. As one of alternative refrigerants for this HFC refrigerant, attempts have been made to use carbon dioxide which has a low global warming potential and is friendly to the global environment. Such carbon dioxide refrigerant is known to be in a supercritical state on the high pressure side of the refrigerant circuit. That is, the refrigerant compressed by the compressor enters a supercritical state and dissipates heat by the radiator. At this time, the refrigerant dissipates heat while maintaining the supercritical state without changing its state. Thereby, the temperature of a refrigerant | coolant will fall by the heat radiation in a radiator. Then, the refrigerant whose temperature has been reduced by the radiator is a two-phase mixed state of gas and liquid in the decompression process in the decompression device, evaporates in the evaporator, and then repeats a cycle returning to the compressor (for example, Patent Document 1).

  By the way, although the carbon dioxide is being generally adopted as a refrigerant for a hot water supply heat pump, when used for cooling applications such as an air conditioner, the efficiency of the refrigeration cycle is significantly reduced compared to the HFC refrigerant. It was not in practical use.

  On the other hand, when introducing the outside air heat exchanged with the evaporator into the conditioned room in the air conditioner, the moisture contained in the outside air becomes a load, so the moisture in the outside air is absorbed by passing through a moisture absorbing member such as a desiccant. Later, attempts have been made to reduce the latent heat load in the evaporator by flowing it into the evaporator.

  The air conditioner provided with the moisture absorbing member allows the moisture absorbing member to pass through and absorbs moisture in the outside air, and then flows into the evaporator, thereby improving the efficiency of the refrigeration cycle using the carbon dioxide refrigerant. It was expected. However, since the moisture removal by the moisture absorbing member of the outside air is an isoenthalpy change, even if the latent heat load can be reduced, the sensible heat load increases correspondingly, that is, the air temperature after moisture removal increases. The total cooling load that must be cooled by the cycle is hardly changed, and as a result, the efficiency of the entire apparatus cannot be effectively improved.

In view of this, an apparatus has been developed in which the outside air from which moisture has been removed by the moisture absorbing member is cooled using a sensible heat rotor and then flows into the evaporator (see, for example, Patent Document 2).
Japanese Patent Publication No. 7-18602 JP 2001-241893 A

  However, when the sensible heat rotor is used as described above, the air that has been recovered by the sensible heat rotor and becomes high temperature is supplied to the radiator, and the temperature of the air that exchanges heat with the refrigerant in the radiator increases. As a result, the heat dissipating ability of the refrigerant in the radiator decreases, and the specific enthalpy at the outlet of the radiator cannot be sufficiently reduced. Therefore, it cannot be said that the apparatus fully utilizes the characteristics of the refrigeration cycle, and the effect of improving the energy consumption efficiency of the entire air conditioner is small.

  The present invention has been made to solve the problems of the related art, and an object of the present invention is to improve the efficiency of the refrigeration cycle and improve the efficiency of the entire air conditioner.

  The air conditioner according to the first aspect of the present invention comprises a compressor, a radiator, a decompressor, and an evaporator. The air conditioner comprises a refrigerant circuit that is operated at a supercritical pressure on the high pressure side, and air that exchanges heat with the evaporator. A moisture absorbing member capable of absorbing and releasing moisture is provided while cooling the chamber to be conditioned. After moisture in the outside air is absorbed by the moisture absorbing member, the moisture is introduced into the evaporator and the air in the chamber to be conditioned is discharged to the outside. The air to be conditioned is ventilated and the moisture absorbed by the hygroscopic member is released by flowing air exchanged with the radiator into the hygroscopic member, and the air flowing into the evaporator through the hygroscopic member A heat exchanger for exchanging heat with the outside air, and a second radiator on the refrigerant downstream side of the radiator to exchange heat between the air discharged from the conditioned room and the second radiator. Features.

  An air conditioner according to a second aspect of the present invention is the first heat radiator in which the radiator is located on the refrigerant upstream side in the first aspect of the invention, and the third radiator located on the refrigerant downstream side of the first radiator. It is characterized in that the air that has been heat-exchanged with the first radiator is caused to flow into the moisture absorbing member, and the third radiator and the outside air are heat-exchanged.

  According to the first aspect of the present invention, the compressor is provided with a compressor, a radiator, a pressure reducing device, and an evaporator, the high pressure side is provided with a refrigerant circuit that is operated at a supercritical pressure, and is conditioned by air exchanged with the evaporator. The chamber is cooled and provided with a moisture absorbing member capable of absorbing and releasing moisture.After the moisture in the outside air is absorbed by the moisture absorbing member, the chamber is ventilated by flowing into the evaporator, and the radiator An air conditioner that releases heat absorbed by the hygroscopic member by flowing heat-exchanged air into the hygroscopic member, wherein the heat exchanger exchanges heat between the air flowing into the evaporator and the outside air via the hygroscopic member. Since it is provided, the moisture in the outside air introduced by the moisture absorbing member can be removed to reduce the latent heat load flowing into the evaporator, and the moisture absorbing member can be regenerated using the exhaust heat of the refrigeration cycle. Become. In particular, by providing a heat exchanger that exchanges heat between the air flowing into the evaporator and the outside air through the moisture absorbing member, the sensible heat load of the air flowing into the evaporator can also be reduced. Thereby, the cooling load of the refrigeration cycle can be reduced, the evaporation temperature and the evaporation pressure of the refrigeration cycle are increased, and the efficiency of the refrigeration cycle can be improved. Therefore, the energy consumption efficiency of the entire air conditioner can be improved. In this case, since the air flowing into the evaporator exchanges heat with the outside air by the heat exchanger, it can be discarded outside without collecting the sensible heat of the air that has passed through the hygroscopic member, and the performance of the refrigerant circuit in which the high pressure side becomes the supercritical pressure It is also possible to prevent the deterioration.

  In addition, the air in the conditioned room is discharged to the outside, and a second radiator is provided on the refrigerant downstream side of the radiator to exchange heat between the air discharged from the conditioned room and the second radiator. The specific enthalpy of the refrigerant at the evaporator inlet can be reduced. This increases the refrigeration effect and improves the efficiency of the refrigeration cycle. Furthermore, by providing the second radiator on the refrigerant downstream side of the radiator, the refrigerant temperature in the radiator increases, and the air temperature for drying and regenerating the moisture absorbing member increases, so the efficiency of the moisture absorbing member improves. . In general, the efficiency of the entire air conditioner can be further improved.

  Furthermore, as in claim 2, the radiator is divided into a first radiator located on the refrigerant upstream side and a third radiator located on the refrigerant downstream side of the first radiator, If the air exchanged with the radiator is allowed to flow into the moisture absorbing member and the third radiator and the outside air are heat exchanged, the air temperature for drying and regenerating the moisture absorbent can be further increased. Efficiency can be further improved, and the efficiency of the entire air conditioner can be further improved.

Hereinafter, the present invention will be described in detail with reference to the drawings .

FIG. 1 is a basic configuration diagram of an air conditioner according to an embodiment of the present invention . In FIG. 1, reference numeral 1 denotes a refrigeration cycle apparatus of the air conditioning apparatus X of the present embodiment, and 2 denotes a conditioned room cooled by the evaporator 16 of the refrigeration cycle apparatus 1. In other words, the air conditioner X cools the conditioned room 2 with air (cold air) cooled by exchanging heat with the evaporator 16 of the refrigeration cycle apparatus 1, introduces outside air, and introduces it from outside air. Ventilation is performed by discharging the air in the conditioned room 2 corresponding to the amount to the outside, and the air quality in the conditioned room 2 is maintained.

In the refrigeration cycle apparatus 1, a refrigerant circuit is configured by sequentially connecting a compressor 10, a radiator 12, a second radiator 13, an expansion valve 14 (decompression device), and an evaporator 16 through refrigerant piping. That is, the refrigerant discharge pipe 32 of the compressor 10 is connected to the inlet of the radiator 12. The second radiator 13 is connected to the outlet side of the radiator 12, and the refrigerant pipe 34 connected to the outlet of the second radiator 13 reaches the expansion valve 14 (the pressure reducing device in the present invention). In this embodiment, the expansion valve 14 is used as the pressure reducing device. However, the pressure reducing device of the present invention may be any device that can depressurize the refrigerant. A tube may be used.

  A refrigerant pipe 35 exiting from the expansion valve 14 is connected to the inlet of the evaporator 16. And the refrigerant | coolant inlet tube 30 of the compressor 10 is connected to the exit of the evaporator 16, and the cyclic | annular closed circuit is comprised. In addition, carbon dioxide is sealed as a refrigerant in the refrigerant circuit. The radiator 12, the second radiator 13 and the evaporator 16 are all heat exchangers for exchanging heat between refrigerant and air. For example, a so-called tube fin type heat exchanger composed of a copper tube and aluminum fins, Alternatively, a so-called microchannel type heat exchanger using an aluminum porous tube is used. In the vicinity of the radiator 12, the second radiator 13, and the evaporator 16, a fan (not shown) is installed as a blowing means.

The radiator 12 is provided outside the conditioned room 2 (outdoors), and is arranged to be able to exchange heat with the outside air. As shown in FIG. 1, the second heat radiator 13 is a second heat radiating means provided on the refrigerant downstream side of the heat radiator 12 of the refrigerant circuit, and discharges air discharged from the conditioned room 2 to the outside. It arrange | positions in the channel | path 42 so that heat exchange with the air discharged | emitted outside from the said to-be-conditioned room 2 concerned is carried out. Further, the evaporator 16 is interposed in an introduction passage 41 for outside air introduced into the conditioned room 2. Therefore, air (external air) exchanged with the refrigerant flowing through the evaporator 16 is introduced into the conditioned room 2 and air exchanged with the refrigerant flowing through the second radiator 13 (inside air of the conditioned room 2). ) Is discharged from the conditioned room 2 to the outside.

  In FIG. 1, 3 is an air passage for flowing the air in the conditioned chamber 2 to the evaporator 16, one end of the air passage 3 is connected to the conditioned chamber 2, and the other end is the introduction passage. 41 in the middle and connected to the windward side of the evaporator 16. As a result, the air in the conditioned room 2 flows into the evaporator 16 through the air passage 3 and the introduction passage 41, and is cooled by exchanging heat with the refrigerant flowing through the evaporator 16. 2 will return. In this way, the air in the conditioned room 2 can be cooled by circulating the air in the conditioned room 2.

  Furthermore, in order to adjust the amount of air (outside air) introduced from outside and the amount of air in the conditioned chamber 2 at the connection point between the introduction passage 41 and the other end of the air passage 3, the amount of air such as a damper (not shown) is adjusted. Means are installed, ventilation operation to introduce air from the outside, cooling operation to circulate only the air in the conditioned room 2 without introducing air from the outside, or conditioned while introducing air from the outside It is assumed that the cooling operation for circulating the air in the chamber 2 can be switched.

  Next, the operation of the air-conditioning apparatus X of the present embodiment having the above configuration will be described with reference to the ph diagram (Mollier diagram) in FIG. In addition, a present Example demonstrates the air_conditionaing | cooling driving | operation which circulates the air of the to-be-conditioned room 2 performing ventilation which introduces air from the outside. First, when the compressor 10 is started by the control means (not shown) of the air conditioner X, the low-temperature and low-pressure refrigerant is sucked into the compressor 10 from the refrigerant introduction pipe 30 (state e6 in FIG. 2). The refrigerant sucked into the compressor 10 is compressed to become high-temperature and high-pressure refrigerant gas, and is discharged from the refrigerant discharge pipe 32. At this time, the high-temperature and high-pressure refrigerant discharged from the refrigerant discharge pipe 32 is in the state a1 in FIG. That is, the refrigerant becomes a supercritical state by compression in the compressor 10.

  In this state, the refrigerant discharged to the refrigerant discharge pipe 32 flows into the radiator 12, where it exchanges heat with the outside air blown by a fan (not shown) to dissipate the heat and exits the radiator 12. At this time, since the refrigerant dissipates heat while maintaining supercriticality in the radiator 12, the temperature of the refrigerant decreases (state a3 in FIG. 2). And the refrigerant | coolant which came out from the heat radiator 12 flows in into the 2nd heat radiator 13, and heat-exchanges with the air in the to-be-conditioned room 2 ventilated with the fan provided in the vicinity of the said 2nd heat radiator 13 there. To further dissipate heat. At this time, the air in the conditioned room 2 blown to the second radiator 13 is air cooled by the evaporator 16 and is lower in temperature than the outside air that exchanges heat with the refrigerant in the radiator 12. The refrigerant radiated by the radiator 12 can be further cooled. Moreover, since the refrigerant dissipates heat while maintaining supercriticality, the temperature of the refrigerant further decreases (state a4 in FIG. 2).

  Thus, the 2nd heat radiator 13 is provided in the refrigerant | coolant downstream of the heat radiator 12, and a refrigerant | coolant can be thermally radiated more by heat-exchanging a refrigerant | coolant and the air from the inside of the chamber 2 to be conditioned. In particular, when the high pressure side of the refrigerant circuit is operated at a supercritical pressure, such as carbon dioxide refrigerant, the temperature decreases with heat dissipation from the refrigerant, so heat is exchanged with the air in the conditioned room 2 having a lower temperature than the outside air. Thus, the temperature of the refrigerant can be further reduced, and the specific enthalpy of the refrigerant can be reduced.

  The refrigerant exiting the second radiator 13 enters the expansion valve 14 through the refrigerant pipe 34 and is decompressed there. At this time, the refrigerant is depressurized from the state a4 in FIG. 2 to the state e5 to be in a gas-liquid two-phase state. In this state, the refrigerant flows into the evaporator 16 and evaporates by taking heat from the air ventilated there (as described above, the mixture of the outside air and the air from the conditioned chamber 2). Further, air (cold air) cooled by removing heat from the refrigerant in the evaporator 16 is discharged into the conditioned room 2. As a result, the interior of the conditioned room 2 is cooled (cooled).

  On the other hand, due to the evaporation in the evaporator 16, the specific enthalpy of the refrigerant changes from the state e5 to the state e6 in FIG. That is, since the specific enthalpy of the refrigerant can be further reduced by the second radiator 13, it is possible to secure a sufficient specific enthalpy difference by evaporation in the evaporator 16.

  In FIG. 2, broken lines connecting f6, c1, c4, and f5 introduce air (outside air) outside the conditioned room 2 directly into the conditioned room 2, and the second radiator 13 is not provided. Or it is the ph diagram of the air conditioning apparatus of the conventional structure which does not introduce external air (that is, does not ventilate) and does not have the 2nd heat radiator 13. FIG. The refrigerant coming out of the radiator 12 is in the state of c4 in FIG. 2, and when it is evaporated in the evaporator 16 in this state, the refrigerant changes from the state of f5 to the state of f6 in FIG. That is, the specific enthalpy of the refrigerant at the inlet of the evaporator 16 is large, and as a result, a sufficient specific enthalpy difference cannot be ensured in the evaporator 16. Further, when the external air (outside air) introduced into the conditioned room 2 is not allowed to flow into the evaporator 16 or when no air is introduced into the conditioned room 2 from the outside, the evaporator 16 Since the air to be heat-exchanged is only the air in the conditioned room 2 having a low temperature, the evaporation temperature and the evaporation pressure of the refrigerant in the evaporator 16 are low.

  Therefore, the broken lines connecting e6, c1, c4, and e′5 in FIG. 2 indicate the case where the outside air introduced into the conditioned chamber 2 is cooled by the evaporator 16 of the refrigerant circuit and then introduced into the conditioned chamber 2. It is a ph diagram of the air conditioning apparatus. As indicated by the broken lines (broken lines connecting e6, c1, c4, and e′5), the outside air introduced into the conditioned room 2 is cooled by the evaporator 16 of the refrigerant circuit and then introduced into the conditioned room 2. As a result, the temperature of the air that exchanges heat with the refrigerant in the evaporator 16 is significantly higher than when only the air in the conditioned chamber 2 flows into the evaporator 16. For this reason, the evaporating temperature and evaporating pressure of the refrigerant in the evaporator 16 can be made higher than the conventional one in which outside air is directly introduced into the conditioned room 2. Therefore, since the temperature and pressure of the refrigerant sucked into the compressor 10 are also increased, the pressure ratio of the compressor 10 is reduced accordingly, the compression work can be reduced, and the efficiency of the refrigeration cycle can be further improved. .

  Furthermore, by providing the second radiator 13 as in the present invention, the specific enthalpy of the refrigerant at the inlet of the evaporator 16 can be reduced. Thereby, since a sufficient specific enthalpy difference can be secured in the evaporator 16, the refrigeration effect of the refrigeration cycle is increased, and the efficiency can be improved. In general, the efficiency of the entire air conditioner X can be improved.

  On the other hand, the refrigerant evaporated in the evaporator 16 (state e6 in FIG. 2) exits the evaporator 16, enters the refrigerant introduction pipe 30, and repeats the cycle of being sucked into the compressor 10.

  In this embodiment, as an independent heat exchanger configured separately from the radiator 12 and the second radiator 13, the radiator 12 is installed outdoors, and the second radiator 13 is connected to the discharge passage 42. However, the present invention is not limited to this, and the radiator 12 and the second radiator 13 may be configured by a single heat exchanger. In this case, the heat exchanger has the refrigerant inlet side, that is, the compressor 10 side arranged outside the room, and the outlet side (expansion valve 14 side) extends from the outside through the wall surface of the discharge passage 42 to discharge the heat. It is configured to be disposed in the passage 42. As a result, it is possible to effectively lower the temperature of the refrigerant whose temperature has been lowered by exchanging heat with the outside air as in the above-described embodiment, by the air (cold air) discharged from the conditioned chamber 2.

Next, the 1st Example of the air conditioning apparatus of this invention is described using FIG. FIG. 3 is a schematic configuration diagram of the air-conditioning apparatus Y of the first embodiment . 3 that have the same reference numerals as those in FIG. 1 have the same or similar effects or actions, and will not be described here.

  The refrigeration cycle apparatus 1 of the air conditioner Y of this embodiment shown in FIG. 3 is similar to the previous embodiment in that it includes a compressor 10, a radiator 12, a second radiator 13, an expansion valve 14 (decompression device), and an evaporator 16. The refrigerant circuit is configured by sequentially connecting the components by refrigerant piping. Further, carbon dioxide is sealed in the refrigerant circuit as a refrigerant as in the above embodiment.

  In FIG. 3, reference numeral 43 denotes an air passage for blowing outside air to the radiator 12 and blowing the air after passing through the radiator 12 to a part of the desiccant rotor 5. That is, the radiator 12 of this embodiment is disposed on the inlet side of the air passage 43 formed outside the conditioned room 2. The desiccant rotor 5 is a rotary moisture absorbing member that includes a moisture absorbing agent that can absorb and release moisture. The hygroscopic agent is made of a material that absorbs moisture at room temperature (or below room temperature) and releases moisture when heated, such as silica gel, zeolite, and cross-linked polyethylene. It is configured by forming. The desiccant rotor 5 rotates around the flow direction of the air from the air passage 43 and the air from the introduction passage, and can sequentially pass through the introduction passage 41 and the air passage 43 arranged in parallel to the introduction passage 41 by rotation. Is arranged.

  That is, paying attention to a part of the desiccant rotor 5, a cycle in which the part is transferred from the introduction passage 41 to the air passage 43 by being rotated by an electric motor (not shown) and is returned to the introduction passage 41 again. In the air passage 43, the air flowing into the desiccant rotor 5 is air heated by the radiator 12 disposed on the inlet side of the air passage 43, and therefore moisture absorbed from outside air in the introduction passage 41. Will be released here. The air that has passed through the desiccant rotor 5 and absorbed the moisture of the desiccant rotor 5, that is, the air containing a large amount of moisture, is discharged from the outlet to the outside of the air passage 43.

  With this configuration, moisture in the air introduced from the outside air into the introduction passage 41 is absorbed by the desiccant rotor 5 located in the introduction passage 41, and the moisture absorbed by the desiccant rotor 5 is absorbed by the air passage 43 in the air passage 43. It can be discharged into the outside air heated by.

  In this way, moisture in the air (in the outside air) introduced into the introduction passage 41 from the outside by the desiccant rotor 5 can be removed, and thereafter the latent heat of the air flowing into the evaporator 16 can be reduced. . In addition, since the air (outside air) heated by exchanging heat with the refrigerant in the radiator 12 is used for drying and regeneration of the desiccant rotor 5 as described above, the exhaust heat of the radiator 12 that has been discharged to the outside in the past. Can be used effectively.

  Further, by providing the second radiator 13 in the refrigerant circuit on the outlet side of the radiator 12, the temperature of the refrigerant flowing through the radiator 12 is increased, and the outside air temperature can also be increased by heat exchange with the refrigerant. . That is, since the air temperature for drying and regenerating the desiccant rotor 5 rises, the efficiency of drying and absorption of the desiccant rotor 5 can be improved. Therefore, the efficiency of the entire air conditioner Y can be further improved. Furthermore, since the drying and absorption efficiency of the desiccant rotor 5 is improved, the same effect can be exhibited even if a desiccant rotor 5 smaller than the conventional desiccant rotor is used. can do. Thereby, it becomes possible to make the whole air conditioning apparatus Y compact.

  Furthermore, by removing moisture in the air that flows into the evaporator 16 by the desiccant rotor 5 in advance, moisture that reaches the evaporator 16 and the filter (not shown) of the evaporator 16 can be recovered in advance. it can. Thereby, water | moisture content adheres to the evaporator 16, its filter, etc., and it can suppress inconveniences, such as generating bacteria from this water | moisture content. Furthermore, since the desiccant rotor 5 allows fresh outside air to be introduced into the room with little energy loss, the air quality in the room can be improved in addition to the effect of suppressing the generation of bacteria.

  Furthermore, since the moisture of the air introduced into the conditioned room 2 can be removed by the desiccant rotor 5 and the humidity can be lowered, the air in the conditioned room 2 can be raised while maintaining comfort. Also by this, since the cooling load can be reduced, energy consumption for cooling can be reduced.

  By the way, it is possible to reduce the latent heat load in the evaporator 16 by removing the moisture with the desiccant rotor 5 as described above. However, the moisture removal by the desiccant rotor 5 of the outside air is an isoenthalpy change. Even though the latent heat load could be reduced, the sensible heat load increased accordingly, that is, the air temperature after moisture removal increased, so the total cooling load that had to be cooled by the refrigeration cycle remained almost unchanged.

  Further, in FIG. 2, the broken lines connecting points a6, d1, d4, and d5 indicate the p− of the conventional air conditioner of the double rotor type (no heat exchanger 7 is installed) using a sensible heat rotor. FIG. That is, only the water is removed by the desiccant rotor 5 and the air cooled by the sensible heat rotor is supplied to the evaporator 16, and the air heated to the heat is recovered by the sensible heat rotor and supplied to the radiator 12. Will be.

  As is apparent from the ph diagram indicated by the broken line, in the conventional double rotor type air conditioner described above, the high-temperature air recovered by the sensible heat rotor is supplied to the radiator 12. As a result, the temperature of the air flowing through the heater 12 rose and the specific enthalpy of the refrigerant at the outlet of the radiator 12 could not be reduced. As a result, it is understood that a sufficient enthalpy difference cannot be secured by evaporation in the evaporator, and the efficiency of the refrigeration cycle is significantly reduced. Therefore, the efficiency of the entire air conditioner cannot be effectively improved. Further, as can be seen from the broken lines connecting points a6, d1, d4, and d5 in FIG. 2, the pressure ratio in the compressor also increases, so the effect of improving the energy consumption efficiency of the entire air conditioner cannot be expected. It was.

  Therefore, in the air conditioner Y of the present embodiment, on the leeward side of the desiccant rotor 5, on the leeward side of the evaporator 16, and in the introduction passage 41 on the leeward side from the connection point of the other end of the air passage 3. A heat exchanger 7 for exchanging heat between the air flowing into the evaporator 16 via the desiccant rotor 5 and the outside air is provided. The heat exchanger 7 is for reducing the sensible heat load of the outside air flowing into the evaporator 16 by exchanging heat between the air after moisture is removed by the desiccant rotor 5 and the outside air. The type of the heat exchanger 7 may be, for example, a plate type or a tube fin type, or may be constituted by a heat pipe or the like, and is not particularly limited. That is, in the present embodiment, after the moisture is removed by the desiccant rotor 5, the air that has been heat-exchanged with the outside air by the heat exchanger 7 is supplied to the evaporator 16.

  Next, the operation of the air conditioning apparatus Y of the present embodiment having the above configuration will be described with reference to FIGS. FIG. 4 is a diagram showing the absolute humidity of air and the dry bulb temperature in each part. First, when the compressor 10 is started by the control means (not shown) of the air conditioner Y, the low-temperature and low-pressure refrigerant is sucked into the compressor 10 from the refrigerant introduction pipe 30 (state a6 in FIG. 2). The refrigerant sucked into the compressor 10 is compressed to become high-temperature and high-pressure refrigerant gas, and is discharged from the refrigerant discharge pipe 32. At this time, the high-temperature and high-pressure refrigerant discharged from the refrigerant discharge pipe 32 is in the state a1 in FIG. That is, the refrigerant becomes a supercritical state by compression in the compressor 10.

  In this state, the refrigerant discharged to the refrigerant discharge pipe 32 flows into the radiator 12, where it exchanges heat with the outside air blown by a fan (not shown) to dissipate the heat and exits the radiator 12. At this time, since the refrigerant dissipates heat while maintaining supercriticality in the radiator 12, the temperature of the refrigerant decreases (state a3 in FIG. 2). And the refrigerant | coolant which came out from the heat radiator 12 flows in into the 2nd heat radiator 13, and heat-exchanges with the air in the to-be-conditioned room 2 ventilated with the fan provided in the vicinity of the said 2nd heat radiator 13 there. To further dissipate heat. At this time, the air in the conditioned room 2 blown to the second radiator 13 is air cooled by the evaporator 16 and is lower in temperature than the outside air that exchanges heat with the refrigerant in the radiator 12. The refrigerant radiated by the radiator 12 can be further cooled. Moreover, since the refrigerant dissipates heat while maintaining supercriticality, the temperature of the refrigerant further decreases (state a4 in FIG. 2).

  Thus, the 2nd heat radiator 13 is provided in the refrigerant | coolant downstream of the heat radiator 12, and a refrigerant | coolant can be thermally radiated more by heat-exchanging a refrigerant | coolant and the air from the inside of the chamber 2 to be conditioned. In particular, when the high pressure side of the refrigerant circuit is operated at a supercritical pressure, such as carbon dioxide refrigerant, the temperature decreases with heat dissipation from the refrigerant, so heat is exchanged with the air in the conditioned room 2 having a lower temperature than the outside air. Thus, the temperature of the refrigerant can be further reduced, and the specific enthalpy of the refrigerant can be reduced.

  The refrigerant exiting the second radiator 13 enters the expansion valve 14 through the refrigerant pipe 34 and is decompressed there. At this time, the refrigerant is depressurized from the state a4 in FIG. 2 to the state a5 to be in a gas-liquid two-phase state. In this state, the refrigerant flows into the evaporator 16 and takes heat from the air that is vented there (the air that has passed through the desiccant rotor 5 and the heat exchanger 7 and the air from inside the conditioned chamber 2). Evaporate.

  On the other hand, the flow of air will be described with reference to FIGS. In this case, the relative humidity of the air introduced from the outside air is 40%, the outside air temperature is + 35 ° C., and this embodiment will be described by taking this temperature and relative humidity as an example. First, outside air having a relative humidity of 40% and an outside air temperature of + 35 ° C. is introduced from the introduction passage 41 (state A1 in FIG. 4). Then, the outside air introduced into the introduction passage 41 passes through the desiccant rotor 5, and moisture is removed by the desiccant rotor 5. As a result, the air after passing through the desiccant rotor 5 is in the state of A2 shown in FIG. 4, and the relative humidity is 10%. Therefore, latent heat in the outside air can be reduced. However, the sensible heat rises as the latent heat is reduced in the desiccant rotor 5, and the air temperature rises to + 50 ° C. in this embodiment.

  In this state, the air in the introduction passage 41 passes through the heat exchanger 7 and is cooled by exchanging heat with the outside air in the heat exchanger 7 to be in the state A3 shown in FIG. At this time, the relative humidity of the air after passing through the heat exchanger 7 is 20%, and the temperature is + 38 ° C. Thereby, the sensible heat of air can also be reduced. Thereafter, the air introduced from the outside air merges with the air circulated from inside the conditioned room 2 to be in the state of A4 shown in FIG. In this embodiment, the relative humidity of the air in the conditioned room 2 is 45% and the temperature is + 27 ° C., so the relative humidity of the air after merging is 35% and the temperature is + 30 ° C.

  The merged air then flows into the evaporator 16. At this time, the air that exchanges heat with the refrigerant in the evaporator 16 is air that has reduced latent heat and sensible heat as described in detail above, and accordingly, the latent heat load and sensible heat load in the evaporator 16 are reduced accordingly. can do. Thereby, the total cooling load that must be cooled by the refrigeration cycle can be reduced, and the energy consumption for cooling can be reduced. Furthermore, since the evaporation temperature and the evaporation pressure of the refrigeration cycle increase, the pressure ratio in the compressor 10 can also be reduced. That is, in the configuration in which the outside air flows into the evaporator 16 as it is without installing the desiccant rotor 5 and the heat exchanger 7, the refrigerant at the inlet of the compressor 10 is in the state e6 and is compressed to a1 by the compressor 10. Although it is necessary, in this embodiment, the refrigerant at the inlet of the compressor 10 is in the state of a6, and the compression work in the compressor 10 can be reduced correspondingly. Thereby, the efficiency of a refrigerating cycle can be improved.

  Further, due to the evaporation in the evaporator 16, the specific enthalpy of the refrigerant changes from the state a5 to the state a6 in FIG. That is, since the specific enthalpy of the refrigerant can be further reduced by the second radiator 13, it is possible to ensure a sufficient specific enthalpy difference by evaporation in the evaporator 16. Thereby, since sufficient specific enthalpy difference can be ensured by evaporation in the evaporator 16, the refrigeration effect of the refrigeration cycle is increased, and the efficiency can be improved.

  Then, the air that has been deprived of heat from the refrigerant that evaporates in the evaporator 16 and cooled is in the state of A5 shown in FIG. The relative humidity of the air after passing through the evaporator 16 is 60%, and the temperature is + 20 ° C. In this way, the air cooled by the evaporator 16 is discharged into the conditioned room 2, thereby cooling (cooling) the conditioned room 2.

  A broken line connecting points a6, c1, c4, and c5 in FIG. 2 is a ph diagram of the air conditioner when the second radiator 13 is deleted from the configuration of the present embodiment. In this case, the refrigerant discharged from the radiator 12 is in the state of c4 in FIG. 2, and when it is evaporated in the evaporator 16 in this state, the refrigerant changes from the state of c5 in FIG. 2 to the state of a6. That is, the specific enthalpy of the refrigerant at the inlet of the evaporator 16 is large, and a sufficient specific enthalpy difference cannot be secured by evaporation in the evaporator 16. Moreover, the pressure ratio of the compressor 10 was also large.

  However, by providing the second radiator 13 as in the present invention, the specific enthalpy of the refrigerant at the inlet of the evaporator 16 can be reduced. Thereby, since sufficient specific enthalpy difference can be ensured by evaporation in the evaporator 16, the refrigeration effect of the refrigeration cycle is increased, and the efficiency can be improved. Also, the pressure ratio can be reduced. Therefore, the coefficient of performance (COP) of the refrigeration cycle represented by the ratio of the refrigeration effect to the compression work can also be improved.

  On the other hand, air in the conditioned room 2 corresponding to the air introduced into the conditioned room 2 is discharged from the conditioned room 2. In this case, the discharged air enters the discharge passage 42, passes through the second radiator 13, is heated by heat exchange with the refrigerant flowing through the second radiator 13, and is in the state of D1 shown in FIG. To D2. At this time, the relative humidity of the air is 30%, the temperature is + 35 ° C., and the air is discharged outside in this state.

  On the other hand, the desiccant rotor 5 that has absorbed moisture in the introduction passage 41 rotates as described above to move from the introduction passage 41 to the air passage 43, and releases moisture to the air heated by the radiator 12. As described above, the second radiator 13 is provided on the outlet side of the refrigerant circuit of the radiator 12 so as to be able to exchange heat with the air in the conditioned room 2. Get higher. Therefore, the outside air flowing in from the inlet of the air passage 43 (in the state of C1 shown in FIG. 4 and the same as the outside air in the state of A1 in FIG. 4 introduced into the introduction passage 41) is used for the radiator 12 as a refrigerant. It is possible to sufficiently heat by heat exchange (state C2 in FIG. 4). At this time, the relative humidity of the air heated by the radiator 12 is 15%, and the temperature is + 55 ° C.

  Further, as described above, the sufficiently heated air flows into the desiccant rotor 5 provided in the air passage 43. And the water | moisture content of the desiccant rotor 5 absorbed in the introduction channel | path 41 is discharge | released in this air (state of C3 shown in FIG. 4). The relative humidity of the air that has received moisture by the desiccant rotor 5 is 35%, and the temperature is + 43 ° C.

  In this way, by using the exhaust heat of the refrigeration cycle, the outside air is heated to a higher temperature and flows into the desiccant rotor 5 provided in the air passage 43, thereby releasing the moisture of the desiccant rotor 5 into the air. Efficient drying and regeneration. Thereby, the water removal efficiency of the desiccant rotor 5 is also improved, and the latent heat load in the evaporator 16 can be reduced.

  Furthermore, by exchanging heat with the outside air in the heat exchanger 7, the sensible heat load in the evaporator 16 can be reduced, the total cooling load of the refrigeration cycle can be reduced, and the evaporation temperature and evaporation pressure of the refrigeration cycle are increased. The efficiency of the refrigeration cycle can be improved. As a result, the energy consumption efficiency of the entire air conditioner Y is improved.

  The relative humidity and temperature of each part described in the present embodiment are merely examples, and it goes without saying that they vary depending on the outside air temperature, the operating state of the refrigeration cycle apparatus 1, the air volume of the fan, or the size and arrangement of the apparatus. In this embodiment, the heat exchanger 7 is a water-cooled heat exchanger that exchanges heat between air and water from the desiccant rotor 5 using a cooling tower or the like, in addition to an air-cooled type that exchanges heat with the outside air. Even it is effective.

  Note that the air conditioner Y of this embodiment includes, for example, a second radiator 13, an indoor unit U1 including an expansion valve 14 and an evaporator 16, a radiator 12, and a heat exchanger as shown in FIG. 7 and an outdoor unit U2 composed of the desiccant rotor 5 may be used. In this case, the indoor unit U1 is installed in the conditioned room 2, and the outdoor unit U2 is installed outside the conditioned room 2. In FIG. 5, the same reference numerals as those in FIGS. 1 to 4 have the same or similar effects or actions, and the description thereof is omitted here.

  FIG. 6 shows an example in which the indoor unit U1 including the second radiator 13, the expansion valve 14, and the evaporator 16 is arranged in the conditioned room 2 as described above. In FIG. 6, reference numeral 20 denotes a cover that covers the indoor unit U <b> 1 disposed in the conditioned room 2 of the air conditioning apparatus Y, and is attached to the wall W of the conditioned room 2. Further, the inside of the cover 20 is partitioned by a partition member 21 into a space 41A on the introduction passage 41 side where the evaporators 16 and 16 are provided and a space 42A on the discharge passage 42 side where the second radiator 13 is provided. In FIG. 6, reference numeral 16 </ b> F denotes a fan as a blowing means for discharging the cold air exchanged with the evaporator 16 installed in the space 41 </ b> A on the introduction passage 41 side into the conditioned room 2.

  The cover 20 has an intake port (not shown) for introducing the air in the conditioned chamber 2 into the space 41A on the introduction passage 41 side in the cover 20, and the space 42A on the discharge passage 42 side in the conditioned chamber 2 inside. (Not shown) for introducing the air, and a discharge port 23 for discharging cold air exchanged with the refrigerant flowing through the evaporator 16 in the space 41 </ b> A in the introduction passage 41 into the conditioned chamber 2. Yes.

  Further, the wall W has a communication hole 24 for communicating the space 42A on the discharge passage 42 side in the cover 20 and the outside of the conditioned chamber 2, and the space 41A on the introduction passage 41 side in the cover 20 and the outside of the conditioned chamber 2 A communication hole 25 that communicates with each other is formed. The air in the conditioned room 2 that has flowed into the space 42 </ b> A in the cover 20 through an intake port (not shown) formed in the cover 20 exchanges heat with the refrigerant in the second radiator 13 provided there. After being heated, the air is discharged out of the conditioned room 2 through the communication hole 24.

  The communication hole 25 is connected to the desiccant rotor 5 of the outdoor unit U2 and the introduction passage 41 for introducing air that has passed through the heat exchanger 7, and moisture is removed from the introduction passage 41 by the desiccant rotor 5. Air radiated by the heat exchanger 7 (air from the outside air) is introduced into the space 41A, is cooled by exchanging heat with the evaporator 16 provided in the space 41A, and then is discharged by the fan 16F. 23 is discharged into the chamber 2 to be conditioned. In FIG. 6, the two evaporators 16 and 16 are provided in the space 41A in the introduction passage 41. However, as shown in FIGS. There is no problem.

Next, the 2nd Example of the air conditioning apparatus of a present Example is described using FIG. FIG. 7 is a schematic configuration diagram of an air conditioner Z according to the second embodiment . 7 having the same reference numerals as those in FIGS. 1 to 6 have the same or similar effects or actions, and the description thereof is omitted here.

  The air conditioner Z of the present embodiment includes a first radiator 12A in which the radiator 12 is located on the refrigerant upstream side and a third radiator 12B located on the refrigerant downstream side of the first radiator 12A. It is divided. And the air heat-exchanged with the 1st heat radiator 12A located in the refrigerant | coolant upstream of the heat radiator 12 flows in into the said desiccant rotor 5, and the air heat-exchanged with the 3rd heat radiator 12B located in the refrigerant | coolant downstream is It is configured to be discharged to the outside without flowing to the desiccant rotor 5.

  In the present embodiment, the first heat radiator 12A and the third heat radiator 12B are constituted by an integrated heat exchanger (heat radiator 12), and these are divided into two on the refrigerant upstream side and the refrigerant downstream side. Shall be classified. In this case, the first radiator 12 </ b> A on the refrigerant upstream side of the radiator 12 is arranged near the inlet in the discharge passage 42, and the third radiator 12 </ b> B on the refrigerant downstream side is arranged in parallel with the discharge passage 42. Arranged in the passage 44. That is, the radiator 12 of the present embodiment extends from one end (first radiator 12A) contacting the one wall surface of the discharge passage 42 to the side of the air passage 44 provided in parallel and extends to the other wall surface of the discharge passage 42. Further, the air passage 44 is disposed so as to pass through one wall surface of the air passage 44 in contact with the wall surface and the other end (third radiator 12B) is in contact with the other wall surface of the air passage 44. Air (outside air) is introduced into the air passage 44 from the outside, and after passing through the third radiator 12B, it can be discharged to the outside.

  The introduction of the outside air into the third radiator 12B may be shared with a fan (not shown) that introduces the outside air into the first radiator 12A, or the fans may be individually attached. When a single fan is shared, a damper may be attached to the air passage 44 to adjust the air volume of the outside air introduced into the third radiator 12B.

  Next, the operation of the air conditioner Z of the present embodiment having the above configuration will be described with reference to the ph diagram of FIG. First, when the compressor 10 is started by the control means (not shown) of the air conditioner Z, the low-temperature and low-pressure refrigerant is sucked into the compressor 10 from the refrigerant introduction pipe 30 (state a6 in FIG. 2). The refrigerant sucked into the compressor 10 is compressed to become high-temperature and high-pressure refrigerant gas, and is discharged from the refrigerant discharge pipe 32. At this time, the high-temperature and high-pressure refrigerant discharged from the refrigerant discharge pipe 32 is in the state a1 in FIG. That is, the refrigerant becomes a supercritical state by compression in the compressor 10.

  In this state, the refrigerant discharged to the refrigerant discharge pipe 32 flows into the first radiator 12A on the refrigerant upstream side of the radiator 12, where heat is exchanged with the outside air blown by a fan (not shown) to dissipate the heat. 2 is a2 state. Further, the refrigerant moves to the third heat radiator 12B on the downstream side of the refrigerant, where heat is exchanged with outside air blown by a fan (not shown) to further dissipate heat, and a state of a3 in FIG. 2 is obtained. At this time, since the refrigerant dissipates heat while maintaining the supercriticality in the radiator 12, the temperature of the refrigerant decreases. And the refrigerant | coolant which came out from the heat radiator 12 flows in into the 2nd heat radiator 13, and heat-exchanges with the air in the to-be-conditioned room 2 ventilated with the fan provided in the vicinity of the said 2nd heat radiator 13 there. To further dissipate heat. At this time, the air in the conditioned room 2 blown to the second radiator 13 is air cooled by the evaporator 16 and is lower in temperature than the outside air that exchanges heat with the refrigerant in the radiator 12. The refrigerant radiated by the radiator 12 can be further cooled. Further, since the refrigerant dissipates heat while maintaining the supercriticality, the temperature of the refrigerant is further lowered to a state of a4 in FIG.

  Thus, the 2nd heat radiator 13 is provided in the refrigerant | coolant downstream of the heat radiator 12, and a refrigerant | coolant can be thermally radiated more by heat-exchanging a refrigerant | coolant and the air from the inside of the chamber 2 to be conditioned. In particular, when the high pressure side of the refrigerant circuit is operated at a supercritical pressure, such as carbon dioxide refrigerant, the temperature decreases with heat dissipation from the refrigerant, so heat is exchanged with the air in the conditioned room 2 having a lower temperature than the outside air. Thus, the temperature of the refrigerant can be further reduced, and the specific enthalpy of the refrigerant can be reduced.

  The refrigerant exiting the second radiator 13 enters the expansion valve 14 through the refrigerant pipe 34 and is decompressed there. At this time, the refrigerant is depressurized from the state a4 in FIG. 2 to the state a5 to be in a gas-liquid two-phase state. In this state, the refrigerant flows into the evaporator 16 and takes heat from the air that is vented there (the air that has passed through the desiccant rotor 5 and the heat exchanger 7 and the air from inside the conditioned chamber 2). Evaporate.

  On the other hand, the air introduced into the conditioned room 2 of the air conditioning apparatus Z, the air circulating in the conditioned room 2, and the flow of air discharged from the conditioned room 2 are shown in the embodiment shown in FIG. Since it is the same as 2, the description is omitted here.

  On the other hand, the desiccant rotor 5 that has absorbed moisture in the introduction passage 41 rotates as described above to move from the introduction passage 41 to the air passage 43, and releases moisture to the air heated by the radiator 12. As described above, the second radiator 13 is provided on the outlet side of the refrigerant circuit of the radiator 12 so as to be able to exchange heat with the air in the conditioned room 2. Get higher. Further, in this embodiment, the radiator 12 is divided into a first radiator 12A on the refrigerant upstream side and a third radiator 12B on the refrigerant downstream side, and heat exchange is performed with the first radiator 12A on the refrigerant upstream side. Since only air is allowed to flow into the desiccant rotor 5, the air temperature for drying and regenerating the desiccant rotor 5 can be further increased.

  That is, the refrigerant flowing through the first radiator 12 </ b> A is the highest temperature refrigerant that has flowed out of the compressor 10. Specifically, in the second embodiment, the refrigerant that exchanges heat with the outside air in the radiator 12 is in the state a3 from the state a1 shown in FIG. 2, whereas the first radiator 12A in the present embodiment. In FIG. 2, the refrigerant that exchanges heat with the outside air is the refrigerant in the state a2 from the state a1 shown in FIG. In other words, the air used for drying and regeneration in the desiccant rotor 5 can be heat-exchanged with the refrigerant in the highest temperature range, so that it can be heated to a higher temperature than in the second embodiment.

  Thereby, since the air temperature for drying and regenerating the desiccant rotor 5 is raised, the drying and absorption efficiency of the desiccant rotor 5 can be further improved. Therefore, the efficiency of the entire air conditioner Z can be further improved. Further, the efficiency of drying and absorption of the desiccant rotor 5 is further improved, so that the same effect can be exhibited even if the desiccant rotor 5 that is smaller than the desiccant rotor of Example 2 is used. . As a result, it is possible to further downsize the desiccant rotor 5 and further downsize the entire air conditioning apparatus.

  The desiccant rotor 5 that has been dried and regenerated again absorbs moisture from the outside air in the introduction passage 41. The air from which moisture has been removed by the desiccant rotor 5 is cooled by exchanging heat with the outside air in the heat exchanger 7 as in the second embodiment. Thereby, the sensible heat load in the evaporator 16 can also be reduced, the cooling load of the refrigeration cycle can be reduced, the evaporation temperature and the evaporation pressure of the refrigeration cycle are increased, and the efficiency of the refrigeration cycle can be improved. Thereby, the energy consumption efficiency of the whole air conditioning apparatus Z can also be improved.

  In the present embodiment, the first heat radiator 12A and the third heat radiator 12B are constituted by an integrated heat exchanger (heat radiator 12), and these are divided into two on the refrigerant upstream side and the refrigerant downstream side. Even though the first heat radiator 12A and the third heat radiator 12B are configured by separate heat exchangers and arranged separately, the present invention is effective. The third radiator 12B of the present embodiment is an air-cooled heat exchanger that exchanges heat between the refrigerant flowing through the third radiator 12B and the outside air, but is not limited thereto, and a cooling tower or the like is used. A water-cooled heat exchanger that exchanges heat between the refrigerant and water may be employed.

It is a schematic block diagram of the air conditioning apparatus used as the basis of the Example of this invention. It is a ph diagram of the refrigerant which flows through the refrigerating cycle device of the air harmony device shown in FIG. It is a schematic block diagram of the air conditioning apparatus of 1st Example of this invention. It is a figure which shows the absolute humidity and dry-bulb temperature of the air which flows through the inside of the air conditioning apparatus of 1st Example of this invention. It is a schematic block diagram which shows an example which comprised the air conditioning apparatus of this invention with the indoor unit and the outdoor unit. It is a figure which shows an example of arrangement | positioning of the indoor unit of the air conditioning apparatus of this invention. It is a schematic block diagram of the air conditioning apparatus of 2nd Example of this invention.

X, Y, Z Air conditioner U1 Indoor unit U2 Outdoor unit W Wall 1 Refrigerating cycle device 2 Room to be conditioned 3 Air passage 4 Damper 5 Desiccant rotor 7 Heat exchanger 10 Compressor 12 Radiator 13 Second radiator 14 Expansion valve (pressure reduction device)
16 Evaporator 20 Cover 21 Partition member 23 Discharge port 24, 25 Communication hole 30 Refrigerant introduction pipe 32 Refrigerant discharge pipe 34, 35 Refrigerant pipe 41 Introduction passage 42 Discharge passage 43, 44 Air passage

Claims (2)

A compressor, a radiator, a decompressor, and an evaporator are provided, and a high-pressure side is provided with a refrigerant circuit that is operated at a supercritical pressure. A moisture absorbing member capable of absorbing and releasing is provided, and after the moisture in the outside air is absorbed by the moisture absorbing member, the moisture is allowed to flow into the evaporator, and the air in the chamber to be conditioned is discharged to the outside. An air conditioner that releases moisture absorbed by the hygroscopic member by flowing into the hygroscopic member air exchanged with the radiator,
The moisture absorbing member through is provided a heat exchanger for the air and the outside air heat exchanger flowing into said evaporator Rutotomoni, a second radiator provided on a refrigerant downstream side of the radiator, the discharged from the conditioning chamber An air conditioner that exchanges heat between the air and the second radiator . The radiator is divided into a first radiator located on the refrigerant upstream side and a third radiator located on the refrigerant downstream side of the first radiator, and heat exchange with the first radiator is performed. 2. The air conditioner according to claim 1, wherein air is caused to flow into the hygroscopic member and heat exchange is performed between the third radiator and outside air.

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