JP2007240128A - Fin for heat exchanger, heat exchanger, and air conditioner - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger fin, a heat exchanger and an air conditioner that improve the operational efficiency of a compressor by providing a dehumidification function of a moisture adsorption means and separating latent heat treatment and sensible heat treatment, and can desorb/regenerate moisture from the moisture adsorption means by means of condensed exhaust heat in a refrigeration cycle while causing moisture to be absorbed onto the moisture adsorption means to prevent an evaporator from frosting. <P>SOLUTION: The surface of the heat exchanger fin 45 supports the moisture adsorption means (for example, mesoporous silica) in which the rate of change in equilibrium moisture uptake with relative humidity in a range from a first relative humidity that is low and a second relative humidity that is higher than the first relative humidity is larger than the rate of change in equilibrium uptake with relative humidity outside the relative humidity range, and the first relative humidity and second relative humidity define a range of 30% to 40%. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a heat exchanger fin, a heat exchanger, and an air conditioner, and in particular, improves the performance of a refrigeration cycle by separately performing a latent heat treatment and a sensible heat treatment, and prevents frost formation on the evaporator. The present invention relates to a heat exchanger fin, a heat exchanger, and an air conditioner.

  Conventionally, there exists an air conditioner having a dehumidifying function. This air conditioner generally includes a refrigeration cycle in which a compressor, a condenser, an expansion valve, and an evaporator are sequentially connected by a refrigerant pipe. The refrigerant pipe is filled with a refrigerant such as a non-azeotropic refrigerant mixture, a pseudo-azeotropic refrigerant mixture, or a single refrigerant. The air conditioner performs heat exchange between the refrigerant and the outside air to cool and heat the refrigerant. It is designed to drive.

  In such an air conditioner, the refrigerant compressed at a high temperature and high pressure by the compressor is discharged from the compressor as a high temperature and high pressure gas refrigerant. This gas refrigerant flows into the condenser and heat-condenses (dissipates heat) with the outside air taken in by the blower to be condensed and liquefied. This liquefied refrigerant is decompressed by the expansion valve to be in a gas-liquid two-phase flow state, and exchanges heat (absorbs heat) with the air taken in by the blower by the evaporator to be evaporated and gasified. At this time, the area to be cooled is cooled. Then, the vaporized refrigerant is sucked into the compressor again. That is, the refrigerant circulates in the refrigeration cycle while repeating heat exchange with the outside air.

  In particular, in a refrigerated / refrigerated warehouse, it is often necessary to control so as to maintain a temperature range lower than 10 [° C.], so that the evaporation temperature in the evaporator becomes lower than 0 [° C.]. For this reason, frost was generated in the evaporator, which caused the cooling capacity of the air conditioner to be reduced. Therefore, a heating device such as a defroster heater is attached to the evaporator so that the defrosting operation (defrosting operation) is periodically performed.

  When the defrosting operation is performed, frost formation on the evaporator can be prevented, but as a result, extra energy is consumed, and the efficiency of the air conditioner cannot be improved. In addition, immediately after the end of the defrosting operation, the temperature in the freezer / refrigerated warehouse that must maintain the predetermined temperature range will rise, increasing the load until the required temperature range is reached, and power consumption Increased further and became inefficient.

  Further, when the air conditioner is a room air conditioner or the like, the cooling load tends to be reduced in the intermediate period of cooling (rainy season, autumn season, etc.). Such an air conditioner normally allows the rotational speed of the compressor to be controlled. When the cooling load is small, the flow rate of the refrigerant circulating in the refrigeration cycle is controlled to be small. As a result, the evaporation temperature rose and the sensible heat of the room could be removed, but the latent heat (water (humidity) in the air) could not be removed. If the room's latent heat could not be removed, the room's relative humidity would increase and discomfort would increase.

  In order to solve such a problem, “a compressor, a radiator, an expansion valve, and a heat absorber are connected in order to form a refrigerant circuit. The refrigerant circuit is filled with CO 2 (carbon dioxide) as a refrigerant. The humidity control mechanism is provided with a desiccant rotor, the heat absorber is supplied with the first air dehumidified by the desiccant rotor, and the desiccant rotor is installed using the second air heated by the radiator. Then, an air conditioner that supplies the dehumidified and cooled first air to the room is disclosed (for example, see Patent Document 1).

  This air conditioner combines a refrigerant refrigerator and a desiccant rotor that is a moisture adsorption means, and before the air flows into the evaporator (heat absorber), the moisture is removed from the air in advance by the desiccant rotor, and is supplied to the evaporator. It prevents frost formation and eliminates defrosting operation. That is, the air dehumidified by the desiccant rotor is supplied to the evaporator, and the high-temperature air heated by the condenser is supplied to the desiccant rotor in order to desorb and regenerate the moisture adsorbed by the desiccant rotor. .

  Moreover, an air conditioner using zeolite as a moisture adsorbing means provided on the surface of the desiccant rotor is disclosed (for example, see Non-Patent Document 1). The moisture adsorption characteristic of this zeolite is that it is necessary to supply air having a relative humidity of several percent or less in order to efficiently desorb and resorb the adsorbed moisture (see isothermal adsorption line A in FIG. 2). That is, in order to reduce the relative humidity of the air, it is necessary to heat the air to a high temperature. Therefore, CO2 (carbon dioxide) is used as the refrigerant so that the heat radiated by the condenser becomes relatively high.

  Furthermore, an air conditioner using silica gel as a moisture adsorbing means provided on the surface of the desiccant rotor is disclosed (for example, see Non-Patent Document 2). It is known that the moisture adsorption characteristics of this silica gel have two types of adsorption characteristics. That is, the water absorption rate is increased in the region where the relative relative humidity is low, and the absorption rate is saturated in the region where the relative relative humidity is high, and the absorption rate is low in the region where the relative relative humidity is low. There are two types, that is, the absorption rate is increased in a high humidity region.

Japanese Patent Laid-Open No. 2001-241893 (pages 6 to 8, FIG. 2) Yoshinori Enomoto, Jiro Okajima, Fumio Matsuoka, Satoshi Akizawa, Takao Kashiwagi, “Dehumidification / Humidification Rotor and System Performance Analysis 1st Report: Theoretical Model” Proc. of the JSRAE Vol. 19, no. 3 (2002) pp. 281-292 (page 287, equation (17)) “About Silica Gel”, Shin-Etsu Chemical Co., Ltd. website, [Search June 1, 2004], Internet <URL: http: // www. shin-etsu-kasei. co. jp / silica. html>

  In the air conditioner described in Patent Document 1, porous inorganic oxides such as zeolite and silica gel are used as the solid adsorbent provided on the surface of the desiccant rotor. When zeolite or silica gel is used as a solid adsorbent, the moisture adsorbed on the zeolite or silica gel is effectively desorbed and regenerated (use the desorbed moisture for humidification, etc.) according to the characteristics of each. Had the problem of not being able to.

  Zeolite used in the air conditioning apparatus described in Non-Patent Document 1 has a rapid increase in the amount of adsorption in the low humidity region, but the amount of increase in the amount of adsorption is small even at high humidity. It has a characteristic that an adsorption loss occurs when it is high. In other words, in order to efficiently desorb and regenerate moisture adsorbed on zeolite, it is necessary to supply air with a relative humidity of several percent or less, and to reduce the relative humidity of air, it is necessary to heat the air to a high temperature. There is.

When zeolite is used as a moisture adsorbing means, high temperature air (for example, 150 ° C.) is required for desorption / regeneration as described above, so that a high temperature is also required for the refrigerant that raises the temperature of the air. Therefore, CO ₂ (carbon dioxide) is often used as a refrigerant because a relatively high refrigerant temperature is easily obtained due to physical properties. When this CO ₂ is used as the refrigerant, a supercritical state exceeding the critical pressure is obtained from the discharge of the compressor until it is sucked into the expansion valve.

When CO ₂ is used as the refrigerant, the high pressure compressed by the compressor is about 100 to 150 [kgf / cm 2], and in the case of a refrigeration cycle that does not exceed the normal critical pressure using HFC (hydrofluorocarbon) as the refrigerant. Since it becomes about 2 times, product cost will rise in order to ensure the pressure | voltage resistance of a compressor, a condenser, and the piping which connects these. In addition, since the regeneration temperature of zeolite is as high as about 150 [° C.], it is necessary to increase the air temperature at the outlet of the condenser, increasing the compression ratio of the compressor and reducing the efficiency of the compressor. there were.

  As described above, the silica gel used in the air conditioner described in Non-Patent Document 1 has two adsorption characteristics. Therefore, silica gels with the same characteristics as zeolites have the same problems as zeolites, with low absorption in regions with low relative relative humidity and absorption in regions with high relative relative humidity. Silica gel, which has the property of increasing the rate, has a problem in that moisture cannot be adsorbed at a standard air relative humidity of 60 [%], and its application is considerably limited.

  The present invention has been made to solve the above-described problems, has a dehumidifying function by a moisture adsorption means, and improves the operation efficiency of the compressor by separately performing the latent heat treatment and the sensible heat treatment. , Heat exchanger fins that can desorb and regenerate moisture from the moisture adsorbing means while adsorbing moisture with the moisture adsorbing means using the condensed exhaust heat in the refrigeration cycle and preventing frost formation on the evaporator, An object is to provide an exchanger and an air conditioner.

  The heat exchanger fin according to the present invention has a rate of change in the equilibrium adsorption amount of moisture relative to the relative humidity in the range of the first relative humidity that is low humidity and the second relative humidity that is higher than the first relative humidity. A moisture adsorbing means having a rate of change of the equilibrium adsorption amount relative to the relative humidity outside the range of the relative humidity and having the first relative humidity and the second relative humidity in the range of 30% to 40% is supported on the surface. It is characterized by that. Moreover, the heat exchanger according to the present invention is characterized by using the above heat exchanger fin.

  An air conditioner according to the present invention is an air conditioner having a refrigeration cycle in which a compressor, a condenser, a heat exchanger, a throttling device, and an evaporator are sequentially connected by a refrigerant pipe to circulate the refrigerant. Thus, the balance of moisture relative to the relative humidity in the range of the first relative humidity, which is low humidity, and the second relative humidity, which is higher than the first relative humidity, is provided on the surface of the heat exchanger fins constituting the heat exchanger. Moisture adsorption means in which the rate of change in adsorption amount is greater than the rate of change in equilibrium adsorption amount relative to relative humidity outside the range of relative humidity, and the first relative humidity and the second relative humidity are in the range of 30% to 40%. Is supported.

  An air conditioner according to the present invention is an air conditioner having a refrigeration cycle in which a compressor, a condenser, a heat exchanger, and an evaporator are sequentially connected by a refrigerant pipe and circulate the refrigerant, The heat exchanger is composed of a first heat exchanger and a second heat exchanger, they are arranged in parallel, and the first opening and closing of the refrigerant pipe between the condenser and the first heat exchanger The surface of the fin for heat exchanger which connects a 2nd on-off valve to the refrigerant | coolant piping between a condenser and a 2nd heat exchanger, and comprises a 1st heat exchanger and a 2nd heat exchanger In addition, the rate of change of the equilibrium adsorption amount of water relative to the relative humidity in the range of the first relative humidity that is low humidity and the second relative humidity that is higher than the first relative humidity is relative to the relative humidity outside the range of relative humidity. It is greater than the rate of change of the equilibrium adsorption amount with respect to the humidity, and the first relative humidity and the second relative humidity There is characterized in that by supporting the water adsorption unit is in the range of 30% to 40%.

  The heat exchanger fin according to the present invention has a rate of change in the equilibrium adsorption amount of moisture relative to the relative humidity in the range of the first relative humidity that is low humidity and the second relative humidity that is higher than the first relative humidity. A moisture adsorbing means having a rate of change of the equilibrium adsorption amount relative to the relative humidity outside the range of the relative humidity and having the first relative humidity and the second relative humidity in the range of 30% to 40% is supported on the surface. Therefore, air having a relative humidity of about 30% is sufficient for desorption / regeneration of the moisture adsorbed on the moisture adsorbing means.

  Since the heat exchanger according to the present invention uses the above heat exchanger fins, air having a relative humidity of about 30% is sufficient for desorption / regeneration of moisture adsorbed on the moisture adsorption means, and constitutes a refrigeration cycle. The moisture adsorbed on the moisture adsorbing means can be desorbed and regenerated by the condensation exhaust heat of the condenser. That is, it is not necessary to provide a desorption / regeneration heater for desorbing moisture adsorbed on the moisture adsorption means, and it is possible to reduce unnecessary power consumption.

  A heat exchanger according to the present invention is an air conditioner having a refrigeration cycle in which a compressor, a condenser, a heat exchanger, a throttling device, and an evaporator are sequentially connected by a refrigerant pipe to circulate the refrigerant. Thus, the balance of moisture relative to the relative humidity in the range of the first relative humidity, which is low humidity, and the second relative humidity, which is higher than the first relative humidity, is provided on the surface of the heat exchanger fins constituting the heat exchanger. Moisture adsorption means in which the rate of change in adsorption amount is greater than the rate of change in equilibrium adsorption amount relative to relative humidity outside the range of relative humidity, and the first relative humidity and the second relative humidity are in the range of 30% to 40%. Therefore, the latent heat can be removed by the moisture adsorption means and the sensible heat can be removed by the refrigeration cycle.

  Therefore, the evaporation temperature of the refrigeration cycle can be set high, the compression ratio can be reduced, and the COP (coefficient of performance) is greatly improved. Further, since the first relative humidity is 30%, air having a relative humidity of about 30% is sufficient to desorb and regenerate the moisture adsorbed by the moisture adsorbing means. Since the desorption / regeneration of the moisture adsorption means can be performed by the condensed exhaust heat, it is not necessary to provide a desorption / regeneration heater, and the power consumption can be greatly reduced. Since the moisture adsorbing means can be desorbed and regenerated by this condensed exhaust heat, the defrosting operation can be eliminated, and the power consumption can be further reduced.

  An air conditioner according to the present invention is an air conditioner having a refrigeration cycle in which a compressor, a condenser, a heat exchanger, and an evaporator are sequentially connected by a refrigerant pipe and circulate the refrigerant, The heat exchanger is composed of a first heat exchanger and a second heat exchanger, they are arranged in parallel, and the first opening and closing of the refrigerant pipe between the condenser and the first heat exchanger The surface of the fin for heat exchanger which connects a 2nd on-off valve to the refrigerant | coolant piping between a condenser and a 2nd heat exchanger, and comprises a 1st heat exchanger and a 2nd heat exchanger In addition, the rate of change of the equilibrium adsorption amount of water relative to the relative humidity in the range of the first relative humidity that is low humidity and the second relative humidity that is higher than the first relative humidity is relative to the relative humidity outside the range of relative humidity. It is greater than the rate of change of the equilibrium adsorption amount with respect to the humidity, and the first relative humidity and the second relative humidity Since but having supported thereon the water adsorption unit is in the range of 30% to 40%, the removal of the latent heat carried by the water adsorption unit, can be performed to remove the sensible heat in the refrigeration cycle.

  Therefore, the evaporation temperature of the refrigeration cycle can be set high, the compression ratio can be reduced, and the COP is greatly improved. Further, since the first relative humidity is 30%, air having a relative humidity of about 30% is sufficient to desorb and regenerate the moisture adsorbed by the moisture adsorbing means. Since the desorption / regeneration of the moisture adsorption means can be performed by the condensed exhaust heat, it is not necessary to provide a desorption / regeneration heater, and the power consumption can be greatly reduced. Since the moisture adsorbing means can be desorbed and regenerated by this condensed exhaust heat, the defrosting operation can be eliminated, and the power consumption can be further reduced.

  In addition, since it is possible to switch between the opening state of the first on-off valve and the opening state of the second on-off valve, it is possible to switch each of the first heat exchanger and the second heat exchanger to the heat of adsorption. As the exchanger and the desorption heat exchanger, they can be used by switching alternately. That is, by switching between the opening state of the first opening / closing valve and the opening state of the second opening / closing valve, the moisture adsorption operation can be continuously performed, and the reliability of the refrigeration cycle is greatly improved. To do.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
Embodiment 1 FIG.
FIG. 1 is a schematic configuration diagram showing a main part of a heat exchanger 40 according to Embodiment 1 of the present invention. Based on FIG. 1, the structure of the heat exchanger 40 which is the characterizing part of this invention is demonstrated. Here, the case where this heat exchanger 40 is a plate fin tube type heat exchanger widely used for a refrigeration apparatus or an air conditioner is shown as an example.

  The heat exchanger 40 is configured using heat exchanger fins 45 (hereinafter simply referred to as fins 45). That is, the heat exchanger 40 is configured by laminating the fins 45. The fin 45 is formed by carrying an adsorbent as a moisture adsorbing means on its surface. Although the amount (thickness) of the adsorbent supported on the fin 45 is not particularly limited, for example, an adsorbent of about 1 mm (millimeter) or less may be supported.

  The heat exchanger 40 is provided with a plurality of heat transfer tubes 46 at predetermined intervals so as to penetrate the fins 45. Here, the case where the six heat transfer tubes 46 are provided so as to penetrate the fins 45 is shown as an example, but the present invention is not limited to this. The heat transfer tube 46 is configured such that a refrigerant flows inside. The refrigerant flowing through the heat transfer tubes 46 exchanges heat with the air flowing between the fins 45.

  Thus, in Embodiment 1, since it is necessary to carry the adsorbent on the heat exchanger 40, a relatively wide fin pitch (4 to 10 mm) that is normally used for a refrigeration apparatus (unit cooler) is used. It is desirable to configure the heat exchanger 40 based on the above. That is, the heat exchanger 40 according to Embodiment 1 may be a commonly used heat exchanger, and does not need to have a special shape or configuration. Therefore, it is possible to reduce labor and cost required for manufacturing the heat exchanger 40.

Next, a method for supporting the adsorbent on the surface of the fin 45 will be described.
As an example of supporting the adsorbent on the surface of the fin 45, there is a method by dipping. Dipping refers to impregnation processing, and is to impregnate a predetermined amount of adsorbent uniformly on the surface of the fin 45 to give a new function. A general procedure for supporting the adsorbent on the surface of the fin 45 by this dipping is shown below.

(1) First, the adsorbent to be carried on the surface of the fin 45 is pulverized to about 10 μm (micrometer).
(2) Next, the pulverized adsorbent and a substance called a binder (bonding agent) are mixed at a predetermined ratio to prepare a mixed solution. The binder is not particularly limited as long as it can adhere the adsorbent to the surface of the fin 45. Further, the mixing ratio of the adsorbent and the binder is not particularly limited, and may be determined in consideration of the amount and thickness of the adsorbent to be carried on the surface of the fin 45.

(3) The heat exchanger 40 assembled by laminating the fins 45 or the fins 45 in the prepared mixed solution is immersed (dipped) a predetermined number of times. The number of times of dipping may be determined depending on whether or not the amount of the adsorbent supported has reached a target amount.
(4) After dipping is performed a predetermined number of times, the fins 45 and the heat exchanger 40 impregnated with the adsorbent are dried.
In this way, the adsorbent can be carried on the surface of the fin 45.

  Another example of supporting the adsorbent on the surface of the fin 45 is a method by electrophoresis. Electrophoresis is a phenomenon in which a charged substance in a solution moves under an electric field, and is generally used in the biochemical field in general. By utilizing this property, the adsorbent can be supported on the surface of the fin 45. That is, by applying an electric potential between the fin 45 carrying the adsorbent and the electrode, the adsorbent particles are moved to the surface of the fin 45 and attached. A general procedure for supporting the adsorbent on the surface of the fin 45 by this electrophoresis is shown below.

(1) First, the adsorbent to be carried on the surface of the fin 45 is pulverized to about 10 μm (micrometer).
(2) Next, the pulverized adsorbent and a substance called a binder (bonding agent) are mixed at a predetermined ratio to prepare a mixed solution. The binder is not particularly limited as long as it can adhere the adsorbent to the surface of the fin 45. Further, the mixing ratio of the adsorbent and the binder is not particularly limited, and may be determined in consideration of the amount and thickness of the adsorbent to be carried on the surface of the fin 45.

(3) The heat exchanger 40 and the electrode assembled by laminating the fin 45 or the fin 45 are immersed in the prepared mixed solution, and a potential is applied between the fin 45 or the heat exchanger 40 and the electrode for a predetermined time. The time for applying this potential may be determined depending on whether or not the adsorbent to be supported has reached a target amount.
(4) The fins 45 and the heat exchanger 40 carrying the target amount of adsorbent are taken out from the mixed solution.
In this way, the adsorbent can be carried on the surface of the fin 45.

  Another example of supporting the adsorbent on the surface of the fin 45 is a method using a spray drying apparatus. The method using a spray drying apparatus is a method in which an adsorbent is sprayed and applied to the surface of the fin 45 so that the adsorbent is supported on the surface of the fin 45. The spray drying device is not a special device, and a device that is generally widely used may be used. A general procedure for supporting the adsorbent on the surface of the fin 45 by this spray drying apparatus will be described below.

(1) First, the adsorbent to be carried on the surface of the fin 45 is pulverized to about 10 μm (micrometer).
(2) Next, the pulverized adsorbent and a substance called a binder (bonding agent) are mixed at a predetermined ratio to prepare a mixed solution. The binder is not particularly limited as long as it can adhere the adsorbent to the surface of the fin 45. Further, the mixing ratio of the adsorbent and the binder is not particularly limited, and may be determined in consideration of the amount and thickness of the adsorbent to be carried on the surface of the fin 45.

(3) The prepared mixed solution is sprayed to the heat exchanger 40 assembled by laminating the fins 45 and the fins 45 by a spray drying device, and continues until a predetermined amount is uniformly attached to the fins 45 and the heat exchanger 40. To do.
(4) The binder is removed by baking the fins 45 and the heat exchanger 40 to which the target amount of adsorbent is attached.
In this way, the adsorbent can be carried on the surface of the fin 45.

  In the first embodiment, three examples of the method for supporting the adsorbent on the surface of the fin 45 have been described. However, the present invention is not limited to this, and the method can support the adsorbent on the surface of the fin 45. I just need it. For example, an adsorbent may be supported on the surface of the fin 45 by a vacuum vapor deposition method, an ion plating method, or the like. In other words, it is desirable to determine the method of loading depending on the type and properties of the adsorbent supported on the fin 45.

Next, the basic concept of the present invention will be briefly described.
In order to improve the moisture adsorption performance of the adsorbent supported on the surface of the fin 45, it is effective to lower the temperature of the air and increase the relative humidity. For this purpose, an adsorbent is supported on the surface of the fin 45 constituting the heat exchanger 40 so that the adsorbent itself and the adsorbed air are cooled at the same time. By doing so, the relative humidity can be increased, and the potential of the adsorption performance of the adsorbent can be maximized.

  In order to improve the moisture desorption performance of the adsorbent supported on the surface of the fin 45, it is effective to increase the temperature of the air and decrease the relative humidity. For this purpose, an adsorbent is supported on the surface of the fin 45 constituting the heat exchanger 40 so that the adsorbent itself and the adsorbed air are heated simultaneously. By doing so, the relative humidity can be reduced, and the potential of the desorption performance of the adsorbent can be maximized.

Next, the adsorbent carried on the surface of the fin 45 will be described.
FIG. 2 is a characteristic diagram showing moisture adsorption characteristics according to the components of the adsorbent that can be carried on the surface of the fin 45. Based on FIG. 2, the adsorbent suitable for carrying on the surface of the fin 45 will be described by comparing each adsorbent. Here, the respective cases using silica gel, zeolite and porous silicon material as the adsorbent are shown. Further, the horizontal axis indicates the relative humidity (%) of the air-conditioned space, and the vertical axis indicates the equilibrium adsorption amount (kg / kg) of moisture.

  In FIG. 2, an isothermal adsorption line A indicates an isothermal adsorption line of silica gel. As a general property, this silica gel is suitable for dehumidification because it has a large adsorption amount in a high humidity range. In FIG. 2, an isothermal adsorption line B indicates an isothermal adsorption line of zeolite. As a general property, this zeolite has a substantially constant adsorption amount in a wide humidity range as opposed to silica gel, and is therefore suitable for humidification applications. In addition, zeolite has a characteristic that the reaction rate of adsorption and desorption is fast.

  In FIG. 2, an isothermal adsorption line C indicates an isothermal adsorption line of a porous silicon material. This porous silicon material is provided with a large number of pores having a hole diameter of about 1.5 to 3.0 nm (nanometers), and is a region where the relative humidity of air is narrow (relative humidity is 30% to 40%). %), The equilibrium adsorption amount shows a characteristic of increasing sharply from, for example, 0.1 kg / kg to 0.4 kg / kg. That is, the slope that is the rate of change of the equilibrium adsorption amount of water relative to the relative humidity in the range of 30% to 40% is the slope that is the rate of change of the equilibrium adsorption amount of moisture to the relative humidity in the range of less than 30% or more than 40%. It has the property of being significantly larger than the above.

  The relative humidity 30% is the first relative humidity (first relative humidity which is low humidity), and the relative humidity 40% is the second relative humidity (second relative humidity which is higher than the first relative humidity). I will call it. Then, it becomes possible to change (increase or decrease) the first relative humidity and the second relative humidity by increasing or decreasing the pore diameter of the porous silicon material. An example of such a porous silicon material is mesoporous silica. Therefore, it is desirable to use this mesoporous silica as an adsorbent.

  This mesoporous silica is a general term for silica (silicon dioxide) -based porous materials having mesopores (diameter 2 to 50 nm) that are uniformly and regularly arranged, and is a cylinder-like fine cell partitioned by a partition wall having a thickness of about 1 nm. The pores have a regular arrangement structure with hexagonal arrangement. In addition, this mesoporous silica has a unique feature that capillary condensation occurs in the mesopores of the mesoporous silica at a relative humidity corresponding to the pore diameter, and exhibits a large adsorption / desorption amount in a specific narrow relative humidity range. Yes.

  Therefore, if the mesoporous silica having such properties is used as an adsorbent that supports the surface of the fin 45, moisture is adsorbed from air having a relative humidity of 40% or more, and the air has a relative humidity of 30% or less. When the temperature is raised to 1, the adsorbed moisture can be desorbed. That is, moisture can be desorbed from the fins 45 even with air heated to about 50 ° C. obtained by heat exchange with the refrigerant flowing in the heat transfer tubes 46 of the heat exchanger 40.

Embodiment 2. FIG.
FIG. 3 is a schematic configuration diagram illustrating a configuration example of the air-conditioning apparatus 100 according to Embodiment 2 of the present invention. Based on FIG. 3, the basic structure of the refrigeration cycle of the air conditioning apparatus 100 will be described. The air conditioner 100 performs a cooling operation and a heating operation using a refrigeration cycle in which a refrigerant is circulated. The air conditioner 100 is assumed to include the heat exchanger described in the first embodiment. Note that the air conditioner 100 may be capable of performing a humidifying operation.

  The air conditioner 100 is configured by sequentially connecting a compressor 10, a condenser 20, a first throttle device 60, a heat exchanger 40, a second throttle device 61, and an evaporator 70 through a refrigerant pipe 1. In general, the compressor 10 and the condenser 20 are built in the outdoor unit, and the first expansion device 60, the heat exchanger 40, the second expansion device 61, and the evaporator 70 are integrated in the indoor unit. Built in. In addition, a humidification unit that performs a humidification operation using moisture adsorbed by the heat exchanger 40 may be mounted on the air conditioner 100.

  The refrigerant pipe 1 is composed of a gas-side refrigerant pipe that conducts a refrigerant that has become a gas, and a liquid-side refrigerant pipe that conducts a refrigerant that has become a liquid. The liquid side refrigerant pipe conducts the refrigerant that has been condensed to become liquid. The gas-side refrigerant pipe conducts the refrigerant that has been evaporated and turned into gas. A blower (not shown) such as a fan for taking air into the condenser 20 is provided in the vicinity of the condenser 20. Similarly, a blower (not shown) such as a fan for taking air into the evaporator 70 and blowing the heat-exchanged air is provided in the vicinity of the evaporator 70. The refrigerant sealed in the refrigerant pipe 1 will be described later in detail.

  The compressor 10 sucks the refrigerant flowing through the refrigerant pipe 1 and compresses the refrigerant to a high temperature / high pressure state. The condenser 20 performs heat exchange between the refrigerant and air to condense and liquefy the refrigerant. The first throttle device 60 is generally composed of a pressure reducing valve or an expansion valve, and decompresses the refrigerant to expand it. For example, it may be composed of an electronic expansion valve or the like. As described with reference to FIGS. 1 and 2, the heat exchanger 40 has an adsorbent as a moisture adsorbing means supported on the surface of the fin 45. The heat exchanger 40 functions to function as an adsorption heat exchanger that adsorbs moisture in the air. It also functions as a desorption heat exchanger that dehumidifies the adsorbed moisture and performs a humidifying operation or the like.

  The second throttle device 61 is generally composed of a pressure reducing valve or an expansion valve, and decompresses the refrigerant to expand it. For example, it may be composed of an electronic expansion valve or the like. The evaporator 70 evaporates the refrigerant by heat exchange between the refrigerant and air. The blower provided in the vicinity of the evaporator 70 takes in the air and supplies the air cooled by the heat exchange in the evaporator 70 to the area to be cooled (in the room, in the refrigerator, in the freezer, etc.). It is. The control of the driving frequency of the compressor 10 and the opening degree of the first throttle device 60 and the second throttle device 61 are performed by a control device (not shown).

Here, operation | movement of the air conditioning apparatus 100 is demonstrated. First, the case where the heat exchanger 40 functions as an adsorption heat exchanger will be described.
The high-temperature and high-pressure refrigerant compressed by the compressor 10 condenses and liquefies into a liquid refrigerant while releasing heat to the outside air by the condenser 20. This liquid refrigerant flows into the first expansion device 60, where it is decompressed and becomes a low-pressure gas-liquid two-phase refrigerant. This gas-liquid two-phase refrigerant flows into the heat exchanger 40 and evaporates while simultaneously cooling the adsorbent and air. That is, the heat exchanger 40 functions as an adsorption heat exchanger. The gas-liquid two-phase refrigerant passes through the second expansion device 61 in the fully opened state and flows into the evaporator 70. The gas-liquid two-phase refrigerant is all vaporized and vaporized by the evaporator 70, becomes a gaseous refrigerant, and is sucked into the compressor 10 again.

Next, the case where the heat exchanger 40 functions as a desorption heat exchanger will be described.
The high-temperature and high-pressure refrigerant compressed by the compressor 10 becomes a gas-liquid two-phase refrigerant while releasing heat to the outside air by the condenser 20. The high-pressure gas-liquid two-phase refrigerant passes through the first expansion device 60 in the fully opened state and flows into the heat exchanger 40. The gas-liquid two-phase refrigerant flowing into the heat exchanger 40 is liquefied while simultaneously heating the adsorbent and air. That is, the heat exchanger 40 functions as a desorption heat exchanger. This liquefied refrigerant is decompressed by the second expansion device 61 to become a low-pressure gas-liquid two-phase refrigerant. The gas-liquid two-phase refrigerant flows into the evaporator 70, where it is all evaporated and gas is converted into a gaseous refrigerant and sucked into the compressor 10 again.

  The air conditioner 100 according to the second embodiment has a latent heat treatment (dehumidifying operation) and a sensible heat treatment (cooling operation or cooling) depending on whether the heat exchanger 40 functions as an adsorption heat exchanger or a desorption heat exchanger. Operation) is separable. That is, the removal of latent heat can be provided by an adsorbent (water adsorption means) carried on the surface of the fin 45, and the removal of sensible heat can be provided by a refrigeration cycle. For this reason, the temperature which evaporates the refrigerant | coolant in the evaporator 70 of a refrigerating cycle can be set high. That is, the evaporation temperature in the evaporator 70 can be set so high that frost is not generated.

  Therefore, if the heat exchanger 40 functions as an adsorption heat exchanger, the evaporation temperature of the evaporator 70 can be set high, and frost can be prevented from being generated in the evaporator 70. In other words, the defrosting operation for removing frost is not necessary, and it is not necessary to provide a defroster heater. Further, the fact that the evaporation temperature of the evaporator 70 can be set high means that it is possible to reduce the compression ratio of the refrigerant in the compressor 10. That is, COP (Coefficient of Performance) can be greatly improved.

  Furthermore, if the heat exchanger 40 is made to function as a desorption heat exchanger, the adsorbed moisture is desorbed by using the condensed exhaust heat in the condenser 20 of the refrigeration cycle, and the moisture is discarded or humidified. It can be used for playback. That is, there is no need to provide heating means such as a regeneration heater for desorbing and regenerating the adsorbed moisture. Therefore, the power consumption required for the heating means becomes unnecessary, and the power consumption can be greatly reduced. In addition, as a typical example of the air conditioning apparatus 100 according to Embodiment 2, it is applied to a refrigerated warehouse as a refrigeration apparatus.

  For example, when the air conditioner 100 is applied to a refrigerated warehouse, the conditions on the outside air side are maintained as a dry bulb temperature of 30 [° C.], a relative humidity of 60 [%], and an absolute humidity of 16.04 [g / kg]. In order to maintain and continue the refrigerator compartment (air-conditioned space) in the refrigerator warehouse under the conditions of a dry bulb temperature of 10 [° C.], a relative humidity of 60 [%], and an absolute humidity of 4.56 [g / kg]. It is preferable to control each device to operate the refrigeration cycle.

  FIG. 4 is a relationship diagram showing the relationship between the evaporation temperature and COP (coefficient of performance: cooling capacity / power consumption). Based on FIG. 4, the relationship between the evaporation temperature and the COP will be described. In FIG. 4, it can be seen that the evaporation temperature and the COP are in a proportional relationship. For example, when the evaporation temperature is 11 [° C.], the COP is about 3.1 ((A) shown in the figure), and when the evaporation temperature is raised to 20 [° C.], the COP is about 3.9 (FIG. As can be seen from FIG. Therefore, if the evaporation temperature can be set high, the COP can be improved accordingly.

Here, the refrigerant | coolant used for the air conditioning apparatus 100 is demonstrated.
Examples of the refrigerant that can be used in the refrigeration cycle of the air conditioner 100 include a non-azeotropic refrigerant mixture, a pseudo-azeotropic refrigerant mixture, and a single refrigerant. Non-azeotropic refrigerant mixture includes R407C (R32 / R125 / R134a) which is an HFC (hydrofluorocarbon) refrigerant. Since this non-azeotropic refrigerant mixture is a mixture of refrigerants having different boiling points, it has a characteristic that the composition ratio of the liquid-phase refrigerant and the gas-phase refrigerant is different. The pseudo azeotropic refrigerant mixture includes R410A (R32 / R125) and R404A (R125 / R143a / R134a) which are HFC refrigerants. This pseudo azeotrope refrigerant has the same characteristic as that of the non-azeotrope refrigerant and has an operating pressure of about 1.6 times that of R22.

  The single refrigerant includes R22, which is an HCFC (hydrochlorofluorocarbon) refrigerant, R134a, which is an HFC refrigerant, and the like. Since this single refrigerant is not a mixture, it has the property of being easy to handle. In addition, carbon dioxide, propane, isobutane, ammonia, etc., which are natural refrigerants, can also be used. R22 represents chlorodifluoromethane, R32 represents difluoromethane, R125 represents pentafluoroethane, R134a represents 1,1,1,2-tetrafluoroethane, and R143a represents 1,1,1-trifluoroethane. ing. Therefore, it is good to use the refrigerant | coolant according to the use and the objective of the air conditioning apparatus 100. FIG.

Embodiment 3 FIG.
FIG. 5 is a schematic configuration diagram illustrating a configuration example of an air-conditioning apparatus 100a according to Embodiment 3 of the present invention. Based on FIG. 5, the basic structure of the refrigerating cycle of the air conditioning apparatus 100a will be described. The air conditioner 100a performs a cooling operation and a heating operation using a refrigeration cycle in which a refrigerant is circulated. This air conditioner 100a is assumed to include the heat exchanger described in the first embodiment. The air conditioner 100a may be capable of performing a humidifying operation. Further, the third embodiment will be described focusing on the differences from the second embodiment, and the same parts as those of the second embodiment will be denoted by the same reference numerals and the description thereof will be omitted.

  The air conditioner 100a includes the heat exchanger 40a (first heat exchanger) and the heat exchanger 40b (second heat exchanger) that carry the adsorbent (moisture adsorption means) described in the first embodiment. I have. The two heat exchangers 40a and 40b are separately incorporated in the indoor unit (see FIG. 5). The air conditioner 100a includes a compressor 10, a condenser 20, an on-off valve 30 as a first on-off valve and an on-off valve 31 as a second on-off valve, and a heat exchange provided in parallel. The heat exchanger 40a and the heat exchanger 40b, the backflow prevention means 50 and the backflow prevention means 51, the expansion device 62, and the evaporator 70 which are arranged in parallel are sequentially connected by the refrigerant pipe 1.

  The refrigerant pipe 1 is branched into a refrigerant pipe 1a and a refrigerant pipe 1b, and the on-off valve 30, the heat exchanger 40a, and the backflow prevention means 50 are connected by the refrigerant pipe 1a, and the on-off valve 31, the heat exchanger 40b, The backflow preventing means 51 is connected by the refrigerant pipe 1b and then joined again. As the refrigerant flowing through the refrigerant pipe 1, the refrigerant described in the second embodiment may be used. Further, the air conditioner 100 a is provided with a temperature / humidity detection means 81 (first temperature / humidity detection means) for detecting the temperature and humidity of the evaporator 70 on the air passage inlet side of the evaporator 70. ing.

  The temperature / humidity detecting means 81 is not particularly limited as long as it can detect temperature and humidity. For example, a temperature sensor such as a thermistor, a thermometer, a humidity sensor, or a hygrometer may be used. Further, the air conditioner 100 a is provided with a control unit 80 that controls the drive frequency of the compressor 10, the opening degree of the opening / closing valve 30 and the opening / closing valve 31, and the opening degree of the expansion device 62.

  The on-off valve 30 and the on-off valve 31 are for adjusting the flow rate of the refrigerant flowing through the refrigerant pipe 1a and the refrigerant pipe 1b, and are not particularly limited in type. The backflow prevention means 50 and the backflow prevention means 51 prevent backflow of the refrigerant flowing through the refrigerant pipe 1a and the refrigerant pipe 1b, and may be constituted by a backflow valve or the like, but are not particularly limited in type. The expansion device 62 is generally configured by a pressure reducing valve or an expansion valve, and expands the pressure by reducing the refrigerant. For example, the expansion device 62 may be configured by an electronic expansion valve. In addition to controlling each device, the control means 80 calculates the relative humidity of the air in the evaporator 70 based on the information from the temperature / humidity detection means 81, and uses the relative humidity as the dew point (dew point temperature). It is designed to be converted, and it may be configured with a microcomputer or the like.

  FIG. 6 is a schematic configuration diagram showing the configuration of the indoor unit 300 in which the evaporator 70 is built. Based on FIG. 6, a basic configuration of the indoor unit 300 will be described. FIG. 6 shows a case where a part of the indoor unit 300 is installed in the freezer (air-conditioned space) 400 and the other part is installed on the outside air 500 side. The indoor unit 300 includes the heat exchanger 40a, the heat exchanger 40b, and the evaporator 70 shown in FIG. In the vicinity of the heat exchanger 40a and the heat exchanger 40b, a blower 90 and a blower 91 such as a centrifugal fan and an axial fan are provided. The indoor unit 300 is provided with a duct 310 so as to communicate with the inside of the freezer 400.

  This indoor unit 300 has a structure that shuts off the heat exchanger 40a and the heat exchanger 40b in a wind path. And the indoor unit 300 can switch an air path, and it becomes possible to make the heat exchanger 40a and the heat exchanger 40b communicate with the inside 400 and the external air 500 by switching an air path. ing. The air path switching is performed by air path switching means 301a and air path switching means 301b, air path switching means 302a and air path switching means 302b, air path switching means 303a and air path switching means 303b, and air path switching means 304a and This is performed by the air path switching means 304b.

Next, the flow of air in the indoor unit 300 will be described.
In FIG. 6, the air path switching means 301a, the air path switching means 302b, the air path switching means 303b, and the air path switching means 304a are in an open state, and the air path switching means 301b, the air path switching means 302a, and the air path switching means 303a. And the air path switching means 304b are closed. When each air path switching means is in such a state, the built-in space of the heat exchanger 40a communicates with the outside air 500, and air flows from the outside air (arrow A). Further, the built-in space of the heat exchanger 40b communicates with the inside of the freezer 400 through the duct 310, and the inside air (for example, the temperature 10 [° C.] and the relative humidity 60 [%]) flows. (Arrow B).

  When the air passage is formed in this way, the heat exchanger 40a functions as a desorption heat exchanger, and the heat exchanger 40b functions as an adsorption heat exchanger. That is, the sensible heat treatment and the latent heat treatment are separated by causing the desorption heat exchanger to function for sensible heat removal and the adsorption heat exchanger to function for latent heat removal. On the other hand, when the open / closed states of the air path switching means are reversed, the internal air flows into the internal space of the heat exchanger 40a, and the internal space of the heat exchanger 40b. The air from the outside flows in. The heat exchanger 40a functions as an adsorption heat exchanger, and the heat exchanger 40b functions as a desorption heat exchanger.

  FIG. 7 is an explanatory diagram illustrating a state where the air path of the indoor unit 300 is switched. FIG. 7 shows a case where a part of the indoor unit 300 is installed in the freezer 400 and the other part is installed on the outside air 500 side. In FIG. 7A, the air path switching means 301a, the air path switching means 302b, the air path switching means 303b, and the air path switching means 304a are closed, and the air path switching means 301b, the air path switching means 302a, It shows that the air path switching means 303a and the air path switching means 304b are in the open state.

  That is, in Fig.7 (a), the built-in space of the heat exchanger 40b is connected with the external air 500, and the air from external air flows in (arrow C). Moreover, the built-in space of the heat exchanger 40a communicates with the inside 400 of the freezer via the duct 310 so that the air inside the compartment flows (arrow D). When the air path is formed in this way, the heat exchanger 40b functions as a desorption heat exchanger, and the heat exchanger 40a functions as an adsorption heat exchanger.

  FIG. 7B shows the air path switching means 301a, the air path switching means 302b, the air path switching means 303b, and the air path switching means 304a in the open state, as in the case shown in FIG. It shows that the switching means 301b, the air path switching means 302a, the air path switching means 303a, and the air path switching means 304b are closed. That is, the internal air flows into the internal space of the heat exchanger 40a, and the outside air flows into the internal space of the heat exchanger 40b. When the air path is formed in this way, the heat exchanger 40b functions as an adsorption heat exchanger, and the heat exchanger 40a functions as a desorption heat exchanger.

  FIG. 8 is a Ph diagram (Mollier diagram) showing the state of the refrigerant in the refrigeration cycle. Based on FIG. 8, the state of the refrigerant in the refrigeration cycle will be described. In this figure, the vertical axis represents absolute pressure (P) and the horizontal axis represents enthalpy (h). In FIG. 8, the portion surrounded by the saturated liquid line and the saturated vapor line indicates a gas-liquid two-phase refrigerant, and the left side of the saturated liquid line indicates a liquefied refrigerant. The right side shows that the refrigerant is gasified. That is, it is known that the refrigerant is a gas refrigerant in the state (1) and the state (5), is a gas-liquid two-phase refrigerant in the state (2) and the state (4), and is a liquid refrigerant in the state (3). You can understand that.

Next, the operation of the air conditioner 100a will be described.
Based on FIG.7 and FIG.8, operation | movement of the air conditioning apparatus 100a is demonstrated. Regarding the operation of the air conditioner 100a when the on-off valve 30 is opened, the on-off valve 31 is closed, the heat exchanger 40a functions as a desorption heat exchanger, and the heat exchanger 40b functions as an adsorption heat exchanger. Shall be explained. Moreover, since the on-off valve 31 is closed, the refrigerant does not flow into the heat exchanger 40b.

  The high-temperature and high-pressure gaseous refrigerant (state (1) shown in FIG. 8) compressed by the compressor 10 flows into the condenser 20. The refrigerant in this state becomes a gas-liquid two-phase refrigerant while dissipating a part of the heat to the outside air in the condenser 20 (state (2) shown in FIG. 8). This high-pressure gas-liquid two-phase refrigerant flows into the heat exchanger 40a carrying the adsorbent. The gas-liquid two-phase refrigerant that has flowed into the heat exchanger 40a blows away moisture adsorbed by the adsorbent by heating the adsorbent (desorption process) to become a liquefied liquid refrigerant (state (3 shown in FIG. 8). )).

  This refrigerant flows through the backflow prevention means 50 and is decompressed by the expansion device 62. The decompressed refrigerant becomes a low-pressure gas-liquid two-phase refrigerant (state (4) shown in FIG. 8). The gas-liquid two-phase refrigerant flows into the evaporator 70 and evaporates by removing heat from the conditioned air to become a low-pressure gas refrigerant (state (5) shown in FIG. 8). This gas refrigerant circulates in the refrigeration cycle so as to be re-inhaled by the compressor 10. Therefore, the cooling / refrigeration operation is performed by circulating the refrigeration cycle while the refrigerant repeatedly changes the state of heat absorption and release.

  FIG. 9 is an air diagram for explaining the operation of the air conditioner 100a. The operation of the above-described air conditioner 100a will be described with reference to the air diagram and the configuration diagram of FIG. In FIG.6 and FIG.9, with respect to the air which passes the heat exchanger 40b connected with the freezer inside 400 side, the state (1) which shows the air before passage of the heat exchanger 40b in FIG. The air immediately after passing is described as a state (2) shown in FIG. 9, and the air immediately after heat exchange with the evaporator 70 is described as a state (3) shown in FIG.

  A case where the heat exchanger 40b adsorbs moisture in the air present in the freezer 400 will be described. The air in the state (1) has a dry bulb temperature of 10 [° C.], a relative humidity of 60 [%], and an absolute humidity of 4.56 [g / kg]. When air in this state is supplied to the heat exchanger 40b, the relative humidity is reduced from 60 [%] to, for example, 30 [%] along the isoenthalpy line, and the absolute humidity is 4.56 [g / kg]. ] To 2.96 [g / kg] and the air in the state (2) in which the dry bulb temperature is increased from 10 [° C.] to 14 [° C.] flows to the evaporator 70. .

  That is, as described in the first embodiment, the adsorbent carried on the heat exchanger 40b has a large amount of moisture that can be adsorbed in a region where the relative humidity is 40% or more, and thus dehumidifies the air in the state (1). It can be done. Then, the air in the state (2) is heat-exchanged by the evaporator 70 to become the air in the state (3). The air in this state (2) is cooled by removing only sensible heat in a state where the absolute humidity is constant, and the relative humidity is less than 100 [%] and the dry bulb temperature is −2 [° C.] (3) Air.

  The inside of the freezer 400 is maintained in a temperature range lower than 10 [° C.], and the evaporation temperature often needs to be set lower than 0 [° C.]. However, the air conditioner 100a is configured so that the refrigeration cycle does not perform the defrosting operation for removing the frost formed on the evaporator 70, so that the evaporation temperature of the evaporator 70 (the temperature 14 [ [° C.]) can be set higher than the dew point temperature (for example, the dew point temperature of the state (2) -2.9 [° C.]).

  In order to increase the evaporation temperature of the evaporator 70, the control means 80 may adjust the evaporation temperature by controlling the opening degree of the expansion device 62, the driving frequency of the compressor 10, the rotational speed of the blower 91, and the like. . Further, as described with reference to FIG. 4, if the evaporation temperature can be set high, the COP can be improved accordingly. Further, since the evaporation temperature of the evaporator 70 can be set to the dew point or higher, no drain is generated. That is, drain piping is not necessary, and the manufacturing cost can be reduced.

  The control means 80 calculates the relative humidity of the air in the evaporator 70 based on the information from the temperature / humidity detection means 81, and converts the relative humidity into a dew point. Based on the result, the dew point is calculated. Should be detected. Then, the air in the state (3) is diffused into the freezer 400 to keep the dry bulb temperature in the freezer 400 at 10 [° C.] or less. In addition, there is a limit to the amount of water that can be adsorbed by the heat exchanger 40b functioning as an adsorption heat exchanger. Therefore, when the control unit 80 determines that the relative humidity on the air channel outlet side of the heat exchanger 40b is equal to or higher than a predetermined threshold based on the detection information from the temperature / humidity detection unit 81, the control valve 80 is opened from the open state. In the closed state, the on-off valve 31 is changed from the closed state to the open state, and the refrigerant flow is switched. Then, a high-temperature and high-pressure gas refrigerant flows into the heat exchanger 40b so that the adsorbent is heated.

  That is, the adsorbed moisture is desorbed by causing the heat exchanger 40b functioning as an adsorption heat exchanger to function as a desorption heat exchanger. When the adsorbent of the heat exchanger 40b is heated, the moisture retained by the adsorbent is released and the adsorbent is regenerated. On the other hand, since the refrigerant flow path is switched, the heat exchanger 40a functions as an adsorption heat exchanger. In the heat exchanger 40a, moisture in the air is adsorbed, and the internal air is dehumidified from the state (1) to the state (2) as shown in FIG.

  In addition, there is a limit to the amount of water that can be adsorbed by the heat exchanger 40a functioning as an adsorption heat exchanger. Therefore, when the control unit 80 determines that the relative humidity on the air channel outlet side of the heat exchanger 40a is equal to or higher than a predetermined threshold based on the detection information from the temperature / humidity detection unit 81, the control valve 80 is switched from the closed state. In the open state, the on-off valve 31 is changed from the open state to the closed state, and the refrigerant flow is switched. Then, a high-temperature and high-pressure gas refrigerant is introduced into the heat exchanger 40a so that the adsorbent is heated.

  As described above, when the air conditioner 100a causes one heat exchanger (heat exchanger 40b) to function as an adsorption heat exchanger, the other heat exchanger (heat exchanger 40a) is a desorption heat exchanger. The function as an adsorption heat exchanger and the function as a desorption heat exchanger are alternately switched according to the amount of moisture adsorbed. Therefore, the humidity (latent heat) of the air in the freezer 400 can be continuously removed. That is, it is possible to continuously remove the humidity of the inside air by appropriately switching the on-off valve 30 and on-off valve 31 and the air path switching means 301a to the air path switching means 304b.

  Table 1 summarizes the control states of the on-off valve 30, the on-off valve 31, and the air path switching means 301a to the air path switching means 304b, and the functions of the heat exchanger 40a and the heat exchanger 40b. In Table 1, pattern 1 shows the case where the heat exchanger 40a functions as an adsorption heat exchanger and the heat exchanger 40b functions as a desorption heat exchanger, as shown in FIG. 7A. The pattern 2 shows the case where the heat exchanger 40a functions as a desorption heat exchanger and the heat exchanger 40b functions as an adsorption heat exchanger, as shown in FIG. 7B. That is, continuous operation is possible by alternately switching between pattern 1 and pattern 2.

  As described above, the moisture adsorption means having the characteristics of the isothermal adsorption line C shown in FIG. 2 is supported on the surface of the fin 45 as an adsorbent, and the heat exchanger 40a and the heat exchanger 40b configured by the fin 45 are provided. Since the refrigeration cycle is configured by using it, it is possible to eliminate the defrosting operation that has frequently occurred in the past, and to further reduce the power consumption associated with the defrosting operation. Further, since the evaporation temperature of the evaporator 70 can be set higher than the dew point temperature, the refrigeration cycle can be operated efficiently.

  As described with reference to FIG. 2, the properties of the adsorbent carried on the surface of the fin 45 are such that air having a relative humidity (first relative humidity) of about 30% is sufficiently desorbed. It can be reproduced. Therefore, in the air conditioner 100a, unlike the case where the adsorbed moisture is heated by a heating means such as a heater, the adsorbent is heated by condensed exhaust heat (heat radiation) from the condenser 20, and the adsorbed moisture is desorbed. it can. That is, it is not necessary to provide a heater, the installation space for the heater can be omitted, and power for heating by the heater becomes unnecessary.

  Moreover, in this air conditioning apparatus 100a, since the evaporation temperature of the evaporator 70 can be set high, the high pressure which the refrigerant | coolant in a refrigerating cycle exceeds a critical pressure is not required. That is, the compressor 10, the condenser 20, and the refrigerant piping 1 (including the refrigerant piping 1 a and the refrigerant piping 1 b) connecting them can be used with low pressure resistance, and the product cost can be reduced. . Moreover, since the compression ratio of the refrigerant in the compressor 10 can be suppressed, the operation efficiency of the compressor 10 can be improved. That is, COP can be greatly improved and energy saving can be achieved.

Embodiment 4 FIG.
FIG. 10 is a schematic configuration diagram illustrating a configuration example of an air-conditioning apparatus 100b according to Embodiment 4 of the present invention. Based on FIG. 10, the fundamental structure of the refrigerating cycle of the air conditioning apparatus 100b is demonstrated. The air conditioner 100b performs a cooling operation and a heating operation using a refrigeration cycle in which a refrigerant is circulated. The air conditioner 100b is assumed to include the heat exchanger described in the first embodiment.

  The air conditioner 100b is intended to realize a high COP by separating the latent heat treatment and the sensible heat treatment. Note that a typical example of the air-conditioning apparatus 100b according to Embodiment 4 is to apply to a room air conditioner or a packaged air conditioner that cools an indoor space. The air conditioner 100b may be capable of performing a humidifying operation. In the fourth embodiment, the differences from the second and third embodiments will be mainly described, and the same parts as those in the second and third embodiments are denoted by the same reference numerals and the description thereof is omitted. It shall be.

  The air conditioner 100b includes a heat exchanger 40c (first heat exchanger) and a heat exchanger 40d (second heat exchanger) that carry the adsorbent (moisture adsorption means) described in the first embodiment. I have. The two heat exchangers 40c and 40d are separately incorporated in the indoor unit (see FIG. 11). The air conditioner 100b includes a compressor 10, a condenser 20, an on-off valve 32 as a first on-off valve and an on-off valve 33 as a second on-off valve, and a heat exchange provided in parallel. The heater 40c and the heat exchanger 40d, the opening / closing valve 34 and the opening / closing valve 35, and the evaporator 70, which are arranged in parallel, are sequentially connected by the refrigerant pipe 1.

  The refrigerant pipe 1 is branched into a refrigerant pipe 1c and a refrigerant pipe 1d, and the open / close valve 32, the heat exchanger 40c, and the open / close valve 34 are connected by the refrigerant pipe 1c, and the open / close valve 33, the heat exchanger 40d, and the open / close valve are connected. The valve 35 is connected by the refrigerant pipe 1d and then joined again. As the refrigerant flowing through the refrigerant pipe 1, the refrigerant described in the second embodiment may be used. Further, the refrigerant pipe 1c and the refrigerant pipe 1d are bypassed from the refrigerant pipe 1c between the on-off valve 32 and the heat exchanger 40c and joined to the refrigerant pipe 1d between the heat exchanger 40d and the on-off valve 35. Pipe 2 (first bypass pipe), a bypass pipe branched from the refrigerant pipe 1d between the on-off valve 33 and the heat exchanger 40d, and joined to the refrigerant pipe 1c between the heat exchanger 40c and the on-off valve 34 3 (second bypass pipe) is provided.

  The bypass pipe 3 is provided with a throttle device 63 (first throttle device) and an on-off valve 36 (third on-off valve). The bypass pipe 2 is provided with a throttle device 64 (second throttle device) and an on-off valve 37 (fourth on-off valve). Further, in the air conditioner 100b, a temperature / humidity detecting means 81 for detecting the temperature and humidity of the evaporator 70 is provided on the air passage inlet side of the evaporator 70, and the temperatures of the heat exchanger 40c and the heat exchanger 40d. And a temperature / humidity detecting means 82 (second temperature / humidity detecting means) for detecting the humidity are provided on the outlet side of the heat exchanger 40c.

  The temperature / humidity detecting means 81 and the temperature / humidity detecting means 82 are not particularly limited as long as they can detect temperature and humidity. For example, a temperature sensor such as a thermistor, a thermometer, a humidity sensor, or a hygrometer may be used. Moreover, although the case where one each of the temperature / humidity detection means 81 and the temperature / humidity detection means 82 is installed is shown as an example, the present invention is not limited to this, and a plurality of them may be installed. Further, the temperature / humidity detection means 82 may be installed on the air path outlet side of each of the heat exchanger 40c and the heat exchanger 40d.

  The air conditioner 100b includes a control for controlling the driving frequency of the compressor 10, the opening of the on-off valve 32 to the on-off valve 37, the opening of the expansion device 63, the expansion device 64, and the expansion device 85 (third expansion device). Means 80a are provided. The on-off valve 32 to the on-off valve 37 are for adjusting the flow rate of the refrigerant flowing through the refrigerant pipe 1a and the refrigerant pipe 1b, and are not particularly limited in kind. The expansion device 63, the expansion device 64, and the expansion device 85 are generally configured by a pressure reducing valve or an expansion valve, and expand the refrigerant by reducing the pressure. For example, the expansion device 63 may be configured by an electronic expansion valve or the like.

  In addition to controlling each device, the control means 80a calculates the relative humidity on the air channel outlet side of the heat exchanger 40c based on the information from the temperature / humidity detection means 82, and calculates the relative humidity as a dew point (dew point temperature). ), And based on the information from the temperature / humidity detection means 81, the relative humidity in the evaporator 70 is calculated and the relative humidity is converted into a dew point (dew point temperature). When the function of the heat exchanger 40c and the function of the heat exchanger 40d are switched, the control unit 80a calculates the relative humidity on the air channel outlet side of the heat exchanger 40d and calculates the relative humidity as a dew point (dew point). Temperature).

  FIG. 11 is a schematic configuration diagram showing a configuration of the indoor unit 300a in which the evaporator 70 is built. Based on FIG. 11, a basic configuration of the indoor unit 300a will be described. The description will focus on the differences from the indoor unit 300 shown in FIG. FIG. 11 shows a case where a part of the indoor unit 300a is installed in the room (air-conditioned space) 401 and the other part is installed on the outside air 500 side. The indoor unit 300a includes the heat exchanger 40c, the heat exchanger 40d, and the evaporator 70 shown in FIG.

  The indoor unit 300a has a structure in which the heat exchanger 40c and the heat exchanger 40d are shut off in a wind path. And the indoor unit 300a can switch an air path, and it becomes possible to connect the heat exchanger 40c and the heat exchanger 40d with the indoor 401 or the external air 500 by switching an air path. Yes. The air path switching is performed by air path switching means 311a and air path switching means 311b, air path switching means 312a and air path switching means 312b, air path switching means 313a and air path switching means 313b, and air path switching means 314a and This is performed by the air path switching means 314b.

Next, the flow of air in the indoor unit 300a will be described.
In FIG. 11, the air path switching means 311a, the air path switching means 312b, the air path switching means 313b, and the air path switching means 314a are in an open state, and the air path switching means 311b, the air path switching means 312a, and the air path switching means 313a. And the air path switching means 314b are in a closed state. When each air path switching means is in such a state, the built-in space of the heat exchanger 40c communicates with the outside air 500, and air flows from the outside air (arrow A). The internal space of the heat exchanger 40d communicates with the room 401 via the duct 310 so that room air (for example, temperature 26 [° C.] and relative humidity 60 [%]) flows in (arrow). B).

  When the air passage is formed in this way, the heat exchanger 40c functions as a desorption heat exchanger, and the heat exchanger 40d functions as an adsorption heat exchanger. That is, the sensible heat treatment and the latent heat treatment are separated by causing the desorption heat exchanger to function for sensible heat removal and the adsorption heat exchanger to function for latent heat removal. On the other hand, when the open / close state of each air path switching means is reversed, the internal air flows into the built-in space of the heat exchanger 40c, and the built-in space of the heat exchanger 40d. The air from the outside flows in. The heat exchanger 40c functions as an adsorption heat exchanger, and the heat exchanger 40d functions as a desorption heat exchanger.

  FIG. 12 is an explanatory diagram illustrating a state where the air path of the indoor unit 300a is switched. FIG. 12 shows a case where a part of the indoor unit 300a is installed in the room 401 and the other part is installed on the outside air 500 side. In FIG. 12A, the air path switching means 311a, the air path switching means 312b, the air path switching means 313b, and the air path switching means 314a are closed, and the air path switching means 311b, the air path switching means 312a, It shows that the air path switching means 313a and the air path switching means 314b are in the open state.

  That is, in Fig.12 (a), the built-in space of the heat exchanger 40d is connected with the external air 500, and the air from external air flows in (arrow C). In addition, the internal space of the heat exchanger 40c communicates with the room 401 via the duct 310 so that room air flows in (arrow D). When the air path is formed in this way, the heat exchanger 40d functions as a desorption heat exchanger, and the heat exchanger 40c functions as an adsorption heat exchanger.

  Further, in FIG. 12B, the air path switching means 311a, the air path switching means 312b, the air path switching means 313b, and the air path switching means 314a are in the open state, as in the case shown in FIG. It shows that the switching means 311b, the air path switching means 312a, the air path switching means 313a, and the air path switching means 314b are closed. That is, room air flows into the built-in space of the heat exchanger 40c, and outside air flows into the built-in space of the heat exchanger 40d. When the air path is formed in this way, the heat exchanger 40d functions as an adsorption heat exchanger, and the heat exchanger 40c functions as a desorption heat exchanger.

  For example, when the air conditioner 100b is applied to a room air conditioner or a packaged air conditioner, the conditions on the outside air 500 side are a dry bulb temperature of 30 [° C.], a relative humidity of 60 [%], and an absolute humidity of 16.04 [g / kg]. In order to maintain and continue the room 401 (air-conditioned space) under the conditions of a dry bulb temperature of 26 [° C.], a relative humidity of 60 [%], and an absolute humidity of 8.74 [g / kg]. It is preferable to control each device to operate the refrigeration cycle.

  FIG. 13 is a Ph diagram (Mollier diagram) showing the state of the refrigerant in the refrigeration cycle. Based on FIG. 13, the state of the refrigerant in the refrigeration cycle will be described. In this figure, the vertical axis represents absolute pressure (P) and the horizontal axis represents enthalpy (h). In FIG. 13, the portion surrounded by the saturated liquid line and the saturated vapor line indicates a gas-liquid two-phase refrigerant, and the left side of the saturated liquid line indicates a liquefied refrigerant. The right side shows that the refrigerant is gasified. That is, it turns out that it is a gas refrigerant in state (1) and state (7), and it turns out that it is a gas-liquid two-phase refrigerant in state (2), state (4), state (5), and state (6). In the state (3), it can be seen that the refrigerant is a liquid refrigerant.

Next, the operation of the air conditioner 100b will be described.
Based on FIG.10 and FIG.13, operation | movement of the air conditioning apparatus 100b is demonstrated. The on-off valve 32, the on-off valve 36, and the on-off valve 35 are opened, the on-off valve 33, the on-off valve 37, and the on-off valve 36 are closed, and the heat exchanger 40c is used as a desorption heat exchanger and the heat exchanger 40d is adsorbed. The operation of the air conditioner 100b when functioning as a heat exchanger will be described.

  The refrigerant in the high-temperature and high-pressure gas state compressed by the compressor 10 (state (1) shown in FIG. 13) flows into the condenser 20. The refrigerant in this state becomes a gas-liquid two-phase refrigerant while dissipating part of the heat to the outside air in the condenser 20 (state (2) shown in FIG. 13). This high-pressure gas-liquid two-phase refrigerant flows into the heat exchanger 40c carrying the adsorbent. The gas-liquid two-phase refrigerant that has flowed into the heat exchanger 40c heats the adsorbent to remove moisture adsorbed on the adsorbent (desorption process), and becomes a liquefied liquid refrigerant (state (3 shown in FIG. 13)). )).

  This refrigerant flows through the on-off valve 36 and is decompressed by the expansion device 63. The decompressed refrigerant becomes a low-pressure gas-liquid two-phase refrigerant (state (4) shown in FIG. 13, first evaporating temperature). The gas-liquid two-phase refrigerant flows into the heat exchanger 40d, and the adsorption performance is improved by cooling the adsorbent at the first evaporation temperature. That is, the moisture in the air is mainly removed (latent heat removal). The gas-liquid two-phase refrigerant that has flowed into the heat exchanger 40d evaporates due to the heat of adsorption and becomes a low-pressure gas-liquid two-phase refrigerant (state (5) shown in FIG. 13). The gas-liquid two-phase refrigerant is depressurized by the expansion device 85, reaches a second evaporation temperature, flows into the evaporator 70, and removes sensible heat in the air (cooling) to become a low-pressure gas refrigerant. (State (6) shown in FIG. 13). This gas refrigerant circulates in the refrigeration cycle so as to be re-inhaled by the compressor 10.

  The air conditioner 100b allows the refrigerant that has passed through one heat exchanger (here, the heat exchanger 40c) to pass through the bypass pipe (here, the bypass pipe 3) and the other heat exchanger (here, It is designed to flow into the heat exchanger 40d). That is, the performance of the adsorbent carried on the surfaces of the fins 45 constituting the heat exchanger 40c and the heat exchanger 40d is improved to improve the refrigerating capacity.

  As shown in FIG. 2, when the moisture adsorption means having the characteristics of the isothermal adsorption line C is carried on the surface of the fin 45 as an adsorbent, the relative humidity around the adsorbent can be obtained by heating the adsorbent. Is small. That is, since the amount of water that can be adsorbed and held by the adsorbent decreases, moisture is released (desorbed) to the surrounding air. If such an adsorbent is used, the relative humidity required for desorption can be made relatively high at 30 [%]. Unlike conventional zeolite (isothermal adsorption line A shown in FIG. 2), the relative humidity does not need to be about 1 [%]. As a result, the adsorbent can be regenerated even at a relatively low temperature. Therefore, it can be easily regenerated even by condensation exhaust heat (about 50 [° C.]) of the refrigeration cycle.

  Further, since the refrigerant passes through one heat exchanger and then flows into the other heat exchanger via the bypass pipe, the adsorbent is directly cooled by the refrigerant in the other heat exchanger. It is possible. Therefore, the air around the adsorbent is also cooled at the same time. Since the adsorbent can be used in a state where the relative humidity is 40% or higher, the performance of the adsorbent can be fully utilized. The amount can be reduced.

  FIG. 14 is an air diagram for explaining the operation of the air conditioner 100b. The operation of the air conditioning apparatus 100b described above will be described using this air diagram and the configuration diagram of FIG. 11 and 14, the air before passing through the heat exchanger 40d is shown in FIG. 14 (1) with respect to the air passing through the heat exchanger 40d communicating with the room 401 side, and the heat exchanger 40d The air immediately after passing will be described as a state (2) shown in FIG. 14, and the air immediately after heat exchange with the evaporator 70 will be described as a state (3) shown in FIG.

  A case where the heat exchanger 40d adsorbs moisture in the air present in the room 401 will be described. The air in the state (1) has a dry bulb temperature of 26 [° C.] and a relative humidity of 60 [%]. When the air in this state is supplied to the heat exchanger 40d, the air in the state (2) flows into the evaporator 70 by isothermal or cooling adsorption in the heat exchanger 40d. That is, as described in the first embodiment, the adsorbent carried on the heat exchanger 40d has a large amount of moisture that can be adsorbed in a region where the relative humidity is 40% or more, and thus dehumidifies the air in the state (1). It can be done.

  Then, the air in the state (2) is heat-exchanged by the evaporator 70 to become the air in the state (3). The air in this state (2) is cooled by removing only sensible heat in a state where the absolute humidity is constant by the evaporator 70, the relative humidity is less than 100%, and the dry bulb temperature is 14 [° C. ] In the state (3). The air in this state (3) is supplied into the room 401.

  In the heat exchanger 40d, it is above the dew point of the intake air (18 [° C.] in this embodiment), and in the evaporator 70, it is above the dew point of the outlet air of the heat exchanger 40d (14 [° C.] in this embodiment). The control means 80a controls the first evaporation temperature and the second evaporation temperature by controlling the opening degree of the expansion device 63 and the expansion device 85, the drive frequency of the compressor 10, the rotational speed of the blower 91, and the like. Adjust it. The detection of the dew point temperature is converted into a dew point by the control means 80a based on the temperature and humidity information detected by the temperature / humidity detection means 81 and the temperature / humidity detection means 82. In this embodiment, a case where the first evaporation temperature is 18 [° C.] and the second evaporation temperature is 14 [° C.] is shown as an example.

  In addition, there is a limit to the amount of moisture that can be adsorbed by the heat exchanger 40d functioning as an adsorption heat exchanger. Therefore, when the control unit 80 determines that the relative humidity in the evaporator 70 is equal to or higher than a predetermined threshold based on the detection information from the temperature / humidity detection unit 81, the control unit 80 sets the on-off valve 32, the on-off valve 37, and the on-off valve 34. From the open state to the closed state, the on-off valve 33, the on-off valve 36, and the on-off valve 35 are changed from the closed state to the open state, and the refrigerant flow is switched. Then, a high-temperature and high-pressure gas refrigerant flows into the heat exchanger 40d so that the adsorbent is heated.

  That is, the adsorbed moisture is desorbed by causing the heat exchanger 40d functioning as an adsorption heat exchanger to function as a desorption heat exchanger. When the adsorbent of the heat exchanger 40d is heated, the water held by the adsorbent is released and the adsorbent is regenerated. On the other hand, since the refrigerant flow path is switched, the heat exchanger 40c functions as an adsorption heat exchanger. In the heat exchanger 40c, moisture in the air is adsorbed, and the indoor air is dehumidified from the state (1) to the state (2) as shown in FIG.

  In addition, there is a limit to the amount of water that can be adsorbed by the heat exchanger 40c functioning as an adsorption heat exchanger. Therefore, when the control unit 80 determines that the relative humidity at the outlet of the heat exchanger 40c is equal to or higher than a predetermined threshold based on the detection information from the temperature / humidity detection unit 81, the on-off valve 33, the on-off valve 36, and the on-off valve 35. Is changed from the open state to the closed state, and the on-off valve 32, the on-off valve 37, and the on-off valve 34 are changed from the closed state to the open state to switch the refrigerant flow. Then, a high-temperature and high-pressure gas refrigerant flows into the heat exchanger 40c so that the adsorbent is heated.

  As described above, when the air conditioner 100b has one heat exchanger (heat exchanger 40d) functioning as an adsorption heat exchanger, the other heat exchanger (heat exchanger 40c) is a desorption heat exchanger. The function as an adsorption heat exchanger and the function as a desorption heat exchanger are alternately switched according to the amount of moisture adsorbed. Therefore, the humidity (latent heat) of the air in the room 401 can be removed continuously.

  On the other hand, from the outside air 500 side, air having a dry bulb temperature of 32 [° C.] and a relative humidity of 6 [%] is supplied to the heat exchanger 40c by the blower 90. At this time, the heat exchanger 40c functions as a desorption heat exchanger, and the adsorbent is heated, the moisture adsorbed and held by the adsorbent is released (desorbed) into the air, and the absolute humidity is increased. The air is again discharged into the outside air 500. Note that the desorbed moisture may be used for humidification. Thus, latent heat is removed by the heat exchanger 40d functioning as an adsorption heat exchanger, and sensible heat can be removed by the refrigeration cycle (evaporator 70). In addition, the desorption / regeneration of the moisture adsorption means can be performed by using the condensed exhaust heat in the condenser 20 of the refrigeration cycle, and the cooling / refrigeration capacity is greatly improved.

  Table 2 summarizes the control states of the on-off valves 32 to 37 and the functions of the heat exchanger 40c and the heat exchanger 40d. In Table 2, pattern 1 shows the case where the heat exchanger 40d functions as an adsorption heat exchanger and the heat exchanger 40c functions as a desorption heat exchanger, as shown in FIG. 12 (b). The pattern 2 shows the case where the heat exchanger 40d functions as a desorption heat exchanger and the heat exchanger 40c functions as an adsorption heat exchanger, as shown in FIG. That is, continuous operation is possible by alternately switching between pattern 1 and pattern 2.

  In pattern 1, the on-off valve 32, the on-off valve 37, and the on-off valve 34 are in an open state, the on-off valve 33, the on-off valve 36, and the on-off valve 35 are in a closed state, and the heat exchanger 40c functions as a desorption heat exchanger, It shows that the heat exchanger 40d functions as an adsorption heat exchanger. On the other hand, in the pattern 2, the on-off valve 33, the on-off valve 36, and the on-off valve 35 are opened, and the on-off valve 32, the on-off valve 37, and the on-off valve 34 are closed. At this time, the heat exchanger 40c is an adsorption heat exchanger. It shows that the heat exchanger 40d functions as a desorption heat exchanger.

  When either the heat exchanger 40c or the heat exchanger 40d functions as a desorption heat exchanger, the refrigerant condenses in the heat exchanger, and the moisture adsorbed and held by the adsorbent is released into the air. In the case where either the heat exchanger 40c or the heat exchanger 40d functions as an adsorption heat exchanger, the refrigerant evaporates in the heat exchanger, the adsorbent is cooled, It adsorbs moisture. That is, the functions of the heat exchanger 40c and the heat exchanger 40d can be switched by controlling the opening degree of each on-off valve and switching the refrigerant flow, and continuously operating while alternately switching between adsorption and desorption. It can be done.

  For example, in a refrigeration cycle of a conventional air conditioner, the condition of the air-conditioned space is a dry bulb temperature of 26 [° C.] and a relative humidity of 60 [%], and the state of the outside air is a dry bulb temperature of 32 [° C.] and a relative humidity of 60 In the case of [%], the balance is adjusted in the vicinity of the condensation temperature 47 [° C.] in the condenser and the evaporation temperature 11 [° C.] in the evaporator, and the sensible heat treatment (cooling operation) and latent heat treatment ( And dehumidifying operation). In such an air conditioner, the evaporation temperature has to be set low, and the efficiency of the refrigeration cycle is poor.

  The air conditioner 100b described in the fourth embodiment can separately perform both the sensible heat treatment (cooling operation) and the latent heat treatment (dehumidification operation) of the air-conditioned space. That is, since the latent heat treatment is performed by the adsorbent (moisture adsorption means) carried on the surface of the fin 45 of each heat exchanger, the refrigeration cycle only needs to be subjected to the sensible heat treatment, and the evaporation temperature can be set high. That is, the conventional evaporating temperature set at 11 [° C.] can be set as high as about 14 [° C.]. As a result, the efficiency of the refrigeration cycle can be greatly improved.

  As shown in FIG. 4, the evaporation temperature and the COP are in a proportional relationship. For example, in the case of Embodiment 4, when the evaporation temperature is 11 [° C.], the COP is about 3.1 ((A) shown in the figure), but this evaporation temperature is set to 14 [° C.]. When it is raised, it can be seen that the COP rises to about 3.3 ((B) shown in the figure). That is, the COP is improved by about 14% just by setting the evaporation temperature to 9 [° C.].

Embodiment 5 FIG.
FIG. 15 is a schematic configuration diagram illustrating a configuration example of an air-conditioning apparatus 100c according to Embodiment 5 of the present invention. Based on FIG. 15, it demonstrates about the fundamental structure of the refrigerating cycle of the air conditioning apparatus 100c. The air conditioner 100c performs a cooling operation and a heating operation using a refrigeration cycle in which a refrigerant is circulated. The air conditioner 100c is assumed to include the heat exchanger described in the first embodiment.

  The air conditioner 100c is intended to realize a high COP by separating the latent heat treatment and the sensible heat treatment. In addition, as a typical example of the air conditioning apparatus 100b according to the fifth embodiment, it is applied to a refrigerated warehouse as a refrigeration apparatus, or applied to a room air conditioner or a packaged air conditioner that cools an indoor space. The air conditioner 100c may be capable of performing a humidifying operation. In the fifth embodiment, differences from the second to fourth embodiments will be mainly described, and the same parts as those in the second to fourth embodiments are denoted by the same reference numerals and the description thereof is omitted. It shall be.

  The air conditioner 100c includes the heat exchanger 40e (first heat exchanger) and the heat exchanger 40f (second heat exchanger) that carry the adsorbent (moisture adsorption means) described in the first embodiment. I have. The two heat exchangers 40e and 40f are separately incorporated in the indoor unit as in the fourth embodiment (see FIG. 10). The air conditioner 100c includes a compressor 10, a condenser 20, an on-off valve 32 and an on-off valve 33 arranged in parallel, a heat exchanger 40e and a heat exchanger 40f arranged in parallel, and three-way arranged in parallel. The valve 38 and the three-way valve 39, the throttle device 63 and the throttle device 64 arranged in parallel, and the evaporator 70 are sequentially connected by the refrigerant pipe 1.

  Similar to the air conditioner 100b according to the fourth embodiment, the refrigerant pipe 1 is branched into a refrigerant pipe 1c and a refrigerant pipe 1d, and the on-off valve 32, the heat exchanger 40e, and the three-way valve 38 are connected to the refrigerant pipe 1c. The on-off valve 33, the heat exchanger 40f and the three-way valve 39 are connected by the refrigerant pipe 1b and then merged again. As the refrigerant flowing through the refrigerant pipe 1, the refrigerant described in the second embodiment may be used. Further, the refrigerant pipe 1c and the refrigerant pipe 1d branch from the refrigerant pipe 1c between the on-off valve 32 and the heat exchanger 40e, and merge into the refrigerant pipe 1d between the heat exchanger 40f and the three-way valve 39. A bypass branching from the bypass pipe 2a (first bypass pipe), the refrigerant pipe 1d between the on-off valve 33 and the heat exchanger 40f, and joining the refrigerant pipe 1c between the heat exchanger 40e and the three-way valve 38 A pipe 3a (second bypass pipe) is provided.

  The bypass pipe 3a is provided with a throttle device 63. The bypass pipe 2a is provided with a throttle device 64. Further, the air conditioner 100 c is provided with temperature / humidity detection means (not shown) for detecting the temperature and humidity of the evaporator 70 on the air passage inlet side of the evaporator 70. The temperature / humidity detecting means is not particularly limited as long as it can detect temperature and humidity. For example, a temperature sensor such as a thermistor, a thermometer, a humidity sensor, or a hygrometer may be used.

  The air conditioner 100c includes the driving frequency of the compressor 10, the opening of the on-off valve 32 and the on-off valve 33, the opening of the throttling device 63, the throttling device 64 and the throttling device 85, and the opening of the three-way valve 38 and the three-way valve 39. Control means (not shown) for controlling the above is provided. The three-way valve 38 and the three-way valve 39 switch the flow of the refrigerant flowing through the refrigerant pipe 1a and the refrigerant pipe 1b to switch the functions (adsorption and desorption) of the heat exchanger 40e and the heat exchanger 40f.

Next, operation | movement of the air conditioning apparatus 100c is demonstrated.
Based on FIG. 15, the operation of the air conditioning apparatus 100c will be described. Regarding the operation of the air conditioner 100c when the on-off valve 32 is opened, the on-off valve 33 is closed, the heat exchanger 40e functions as a desorption heat exchanger, and the heat exchanger 40f functions as an adsorption heat exchanger. Shall be explained.

  The high-temperature and high-pressure gaseous refrigerant compressed by the compressor 10 flows into the condenser 20. The refrigerant in this state becomes a gas-liquid two-phase refrigerant while radiating part of the refrigerant to the outside air in the condenser 20. This high-pressure gas-liquid two-phase refrigerant flows into the heat exchanger 40e carrying the adsorbent. The gas-liquid two-phase refrigerant that has flowed into the heat exchanger 40e heats the adsorbent to remove moisture adsorbed on the adsorbent (desorption process), and becomes a liquefied liquid refrigerant.

  The flow direction of this refrigerant is determined by the control of the three-way valve 38. For example, if it is controlled to flow through the bypass pipe 3 a, the refrigerant is decompressed by the expansion device 63. The decompressed refrigerant becomes a low-pressure gas-liquid two-phase refrigerant. And this gas-liquid two-phase refrigerant | coolant flows in into the heat exchanger 40f, and improves adsorption | suction performance by cooling an adsorbent. That is, the moisture in the air is mainly removed (latent heat removal). The gas-liquid two-phase refrigerant that has flowed into the heat exchanger 40f evaporates due to the heat of adsorption, and becomes a low-pressure gas-liquid two-phase refrigerant. This gas-liquid two-phase refrigerant is decompressed by the expansion device 85, flows into the evaporator 70, and takes sensible heat in the air (cooling) to become a low-pressure gas refrigerant. This gas refrigerant circulates in the refrigeration cycle so as to be re-inhaled by the compressor 10.

  The air conditioner 100c allows the refrigerant that has passed through one heat exchanger (here, the heat exchanger 40e) to pass through the bypass pipe (here, the bypass pipe 3a) and the other heat exchanger (here, It is designed to flow into the heat exchanger 40f). That is, the performance of the adsorbent carried on the surfaces of the fins 45 constituting the heat exchanger 40e and the heat exchanger 40f is enhanced to improve the refrigerating capacity.

  As shown in FIG. 2, when the moisture adsorption means having the characteristics of the isothermal adsorption line C is carried on the surface of the fin 45 as an adsorbent, the relative humidity around the adsorbent can be obtained by heating the adsorbent. Is small. That is, since the amount of water that can be adsorbed and held by the adsorbent decreases, moisture is released (desorbed) to the surrounding air. If such an adsorbent is used, the relative humidity required for desorption can be made relatively high at 30 [%]. Unlike conventional zeolite (isothermal adsorption line A shown in FIG. 2), the relative humidity does not need to be about 1 [%]. As a result, the adsorbent can be regenerated even at a relatively low temperature. Therefore, it can be easily regenerated even by condensation exhaust heat (about 50 [° C.]) of the refrigeration cycle.

  Further, since the refrigerant passes through one heat exchanger and then flows into the other heat exchanger via the bypass pipe, the adsorbent is directly cooled by the refrigerant in the other heat exchanger. It is possible. Therefore, the air around the adsorbent is also cooled at the same time. Since the adsorbent can be used in a state where the relative humidity is 40% or higher, the performance of the adsorbent can be fully utilized. The amount can be reduced.

  In this way, the fin 45 carrying the adsorbent having the characteristics of the isothermal adsorption line C shown in FIG. 2 is used in the heat exchanger 40e and the heat exchanger 40f in the refrigeration cycle. By combining the cycle, it is possible to separate the sensible heat treatment and the latent heat treatment and improve the refrigerating capacity. That is, since the evaporation temperature can be set higher than the dew point of the intake air temperature by the evaporator 70 and the compression ratio of the compressor 10 can be reduced correspondingly, the performance of the refrigeration cycle is dramatically improved.

  In addition, regeneration of a conventional adsorbent (for example, zeolite) required a high temperature of 100 [° C.]. By using an adsorbent having the characteristics of the isothermal adsorption line C shown in FIG. The adsorbent can be heated by using the condensed exhaust heat of the refrigeration cycle and can be easily regenerated. That is, it is not necessary to install a heater, and it is possible to reduce the electric power used for the heater, thereby realizing space saving and energy saving.

  In each embodiment, the type of the compressor 10 is not particularly limited, but an inverter compressor capable of capacity control or a constant speed compressor performing constant speed operation may be used. Moreover, in each embodiment, although the case where one unit of the compressor 10 was provided in the refrigerating cycle was shown as an example, it is not limited to this, You may provide a some compressor. In this case, it is preferable to perform multi-control for the number of compressors provided by the control means 80.

  In each embodiment, the case where the control means 80 and the control means 80a control the opening degree of each on-off valve, the driving frequency of the compressor 10, the opening degree of each throttle device, and the opening degree of each three-way valve will be described as an example. However, the present invention is not limited to this. Control means may be provided for each device. Further, in each embodiment, the case where one temperature / humidity detection unit 81 is provided on the inlet side of the evaporator 70 is described as an example, but the present invention is not limited to this. For example, the temperature detection means and the humidity detection means may be provided separately, or a plurality of them may be provided. Moreover, you may provide the pressure detection means which detects the pressure of a refrigerant | coolant in the vicinity of each apparatus.

  In addition, although the air conditioning apparatus 100-the air conditioning apparatus 100c demonstrated to the example the case where it applied to a freezing apparatus, a room air conditioner, a packaged air conditioner, etc., it is not limited to this. For example, the air conditioning apparatus 100 to the air conditioning apparatus 100c can be applied to a refrigerator, a humidifier, a humidity control apparatus, or the like. That is, it is only necessary to determine the refrigerant to be used according to the purpose and application to be applied, or to determine the air path and flow path in the refrigeration cycle.

FIG. 2 is a schematic configuration diagram illustrating a main part of a heat exchanger according to Embodiment 1. It is a characteristic view which shows the water | moisture-content adsorption | suction characteristic according to the component of adsorption agent. FIG. 6 is a schematic configuration diagram illustrating a configuration example of an air-conditioning apparatus according to Embodiment 2. It is the relationship figure which showed the relationship between evaporation temperature and COP. FIG. 6 is a schematic configuration diagram illustrating a configuration example of an air-conditioning apparatus according to Embodiment 3. It is the schematic block diagram which showed the humidification unit of the air conditioning apparatus in three dimensions. It is explanatory drawing which shows the state which switched the air path of the indoor unit. It is a Ph diagram which shows the state of the refrigerant in a refrigerating cycle. It is an air line figure for demonstrating operation | movement of an air conditioning apparatus. It is a schematic block diagram which shows the structural example of the air conditioning apparatus which concerns on Embodiment 4. FIG. It is a schematic block diagram which shows the structure of the indoor unit in which the evaporator was incorporated. It is explanatory drawing which shows the state which switched the air path of the indoor unit. It is a Ph diagram which shows the state of the refrigerant in a refrigerating cycle. It is an air line figure for demonstrating operation | movement of an air conditioning apparatus. It is a schematic block diagram which shows the structural example of the air conditioning apparatus which concerns on Embodiment 5. FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Refrigerant piping, 1a Refrigerant piping, 1b Refrigerant piping, 1c Refrigerant piping, 1d Refrigerant piping, 2 Bypass pipe, 2a Bypass pipe, 3 Bypass pipe, 3a Bypass pipe, 10 Compressor, 20 Condenser, 30 On-off valve, 31 Open / close Valve, 32 On-off valve, 33 On-off valve, 34 On-off valve, 35 On-off valve, 36 On-off valve, 37 On-off valve, 38 Three-way valve, 39 Three-way valve, 40 Heat exchanger, 40a Heat exchanger, 40b Heat exchanger, 40c Heat exchanger, 40d heat exchanger, 40e heat exchanger, 40f heat exchanger, 45 fin, 46 heat transfer tube, 50 backflow prevention means, 51 backflow prevention means, 60 throttling device, 61 throttling device, 62 throttling device, 63 throttling Device, 64 throttle device, 70 evaporator, 80 control means, 80a control means, 81 temperature / humidity detection means, 85 throttle device, 90 blower, 91 blower, 100 air conditioner, 00a Air conditioner, 100b Air conditioner, 300 Indoor unit, 300a Indoor unit, 301a Air path switching means, 301b Air path switching means, 302a Air path switching means, 302b Air path switching means, 303a Air path switching means, 303b Wind Path switching means, 304a air path switching means, 304b air path switching means, 311a air path switching means, 311b air path switching means, 312a air path switching means, 312b air path switching means, 313a air path switching means, 313b air path switching Means, 314a Air path switching means, 314b Air path switching means, 400 Inside the freezer, 401 Indoor, 500 Outside air.

Claims (16)

The rate of change of the equilibrium adsorption amount of water relative to the relative humidity in the range of the first relative humidity that is low humidity and the second relative humidity that is higher than the first relative humidity is the relative humidity outside the range of the relative humidity. A moisture adsorbing means having a rate greater than the rate of change of the equilibrium adsorption amount with respect to the water and the first relative humidity and the second relative humidity ranging from 30% to 40% is supported on the surface. Heat exchanger fins. The heat exchanger fin of Claim 1 was used. The heat exchanger characterized by the above-mentioned. An air conditioner having a refrigeration cycle in which a compressor, a condenser, a heat exchanger, a throttling device, and an evaporator are sequentially connected by a refrigerant pipe and circulate the refrigerant,
Equilibrium adsorption of moisture relative to the relative humidity in the range of the first relative humidity which is low humidity and the second relative humidity which is higher than the first relative humidity on the surface of the heat exchanger fins constituting the heat exchanger The rate of change of the amount is greater than the rate of change of the equilibrium adsorption amount relative to the relative humidity outside the range of the relative humidity, and the first relative humidity and the second relative humidity are in the range of 30% to 40%. An air conditioner characterized by supporting a moisture adsorbing means. An air conditioner having a refrigeration cycle in which a compressor, a condenser, a heat exchanger, and an evaporator are sequentially connected by a refrigerant pipe and circulate the refrigerant,
The heat exchanger is composed of a first heat exchanger and a second heat exchanger, and they are arranged in parallel.
A first on-off valve is connected to the refrigerant pipe between the condenser and the first heat exchanger, and a second on-off valve is connected to the refrigerant pipe between the condenser and the second heat exchanger. And
A first relative humidity that is low humidity and a second relative humidity that is higher than the first relative humidity are formed on the surfaces of the fins for the heat exchanger that constitute the first heat exchanger and the second heat exchanger. And the change rate of the equilibrium adsorption amount of water with respect to the relative humidity in the range is larger than the change rate of the equilibrium adsorption amount with respect to the relative humidity outside the range of the relative humidity, and the first relative humidity and the second An air conditioner characterized by carrying a moisture adsorbing means having a relative humidity in the range of 30% to 40%. Control means for controlling the opening degree of the first on-off valve and the second on-off valve;
A first temperature / humidity detection means for detecting the temperature and humidity of the evaporator is provided on the air passage inlet side of the evaporator,
The control means includes
Calculate the relative humidity of the air in the evaporator based on the information from the first temperature / humidity detection means,
Either the first heat exchanger or the second heat exchanger functions as an adsorption heat exchanger and the other functions as a desorption heat exchanger according to the calculated relative humidity. The air conditioner according to claim 4, wherein the opening degree of the on-off valve and the second on-off valve is controlled. The control means includes
Depending on the calculated relative humidity,
By controlling one of the first on-off valve and the second on-off valve to an open state and the other on-off valve to a closed state, the first heat exchanger or the second on-off valve is controlled. The air conditioner according to claim 5, wherein the flow path of the refrigerant flowing into the heat exchanger is alternately switched. The control means also controls the drive frequency of the compressor,
The control means includes
Convert the relative humidity into a dew point,
The drive frequency of the compressor and the opening degrees of the first on-off valve and the second on-off valve are controlled so that the evaporation temperature of the evaporator is equal to or higher than the dew point. The air conditioning apparatus according to 5 or 6. Second temperature / humidity detection means for detecting the temperature and humidity of the first heat exchanger and the second heat exchanger is used as the wind of the first heat exchanger and the second heat exchanger. Provided on the road exit side,
The control means includes
Calculate the relative humidity of air in the first heat exchanger and the second heat exchanger based on information from the second temperature / humidity detection means,
Convert the result into a dew point,
The drive frequency of the compressor and the opening of the first on-off valve and the second on-off valve are set so that the set temperatures of the first heat exchanger and the second heat exchanger are equal to or higher than the dew point. The air conditioner according to any one of claims 5 to 7, wherein the air conditioner is controlled. A first bypass pipe for branching a refrigerant pipe between the first on-off valve and the first heat exchanger and joining the refrigerant pipe on the refrigerant outlet side of the second heat exchanger;
Providing a second bypass pipe for branching a refrigerant pipe between the second on-off valve and the second heat exchanger and joining the refrigerant pipe on the refrigerant outlet side of the first heat exchanger;
The first throttling device and the third on-off valve are arranged in the first bypass pipe, and the second throttling device and the fourth on-off valve are arranged in series on the second bypass pipe, respectively. The air conditioning apparatus according to claim 4. The opening of the first on-off valve and the second on-off valve; the opening of the first throttling device and the second throttling device; the third on-off valve and the fourth on-off valve; Control means for controlling the opening;
A first temperature / humidity detection means for detecting the temperature and humidity of the evaporator is provided on the air passage inlet side of the evaporator,
The control means includes
Calculate the relative humidity of the air in the evaporator based on the information from the first temperature / humidity detection means,
Either the first heat exchanger or the second heat exchanger functions as an adsorption heat exchanger and the other functions as a desorption heat exchanger according to the calculated relative humidity. The opening degree of the on-off valve and the second on-off valve, the opening degree of the first throttling device and the second throttling device, and the opening degree of the third on-off valve and the fourth on-off valve The air conditioner according to claim 9, wherein the opening degree is controlled. The control means includes
Depending on the calculated relative humidity,
By controlling one of the first on-off valve and the second on-off valve to an open state and the other on-off valve to a closed state, the first heat exchanger or the second heat exchange Alternately switching the flow path of the refrigerant flowing into the container,
The opening degree of the third on-off valve and the fourth on-off valve is controlled in accordance with the state of the opening degree of the first on-off valve and the second on-off valve. Air conditioner. The control means also controls the drive frequency of the compressor,
The control means includes
Convert the relative humidity into a dew point,
The driving frequency of the compressor, the opening degrees of the first on-off valve and the second on-off valve, the first throttling device, and the first throttling temperature so that the evaporation temperature of the evaporator is equal to or higher than the dew point. The air conditioner according to claim 10 or 11, wherein an opening degree of the throttle device 2 and an opening degree of the third on-off valve and the fourth on-off valve are controlled. Second temperature / humidity detection means for detecting the temperature and humidity of the first heat exchanger and the second heat exchanger is used as the wind of the first heat exchanger and the second heat exchanger. Provided on the road exit side,
The control means includes
Calculate the relative humidity in the first heat exchanger and the second heat exchanger based on the information from the second temperature / humidity detection means,
Convert the result into a dew point,
The drive frequency of the compressor and the opening of the first on-off valve and the second on-off valve are set so that the set temperatures of the first heat exchanger and the second heat exchanger are equal to or higher than the dew point. The degree of opening, the opening degree of the first throttling device and the second throttling device, and the opening degree of the third on-off valve and the fourth on-off valve are controlled. The air conditioning apparatus according to any one of 12. The first heat exchanger and the second heat exchanger are separately incorporated in the indoor unit,
The control means includes
The air conditioner according to any one of claims 4 to 13, wherein the air path in the indoor unit is switched in accordance with the opening states of the first on-off valve and the second on-off valve. . The air conditioner according to any one of claims 3 to 14, wherein the moisture adsorbing means is composed of a silicon material provided with a large number of pores having a hole diameter of 1.5 to 3.0 nanometers. . The air conditioner according to claim 15, wherein the silicon material is mesoporous silica.

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