JP3815484B2 - Heat exchanger - Google Patents

Abstract

The difference between the linear thermal expansion coefficient of a fin (57) and that of an absorbent layer (58) is set smaller than the difference between the linear thermal expansion coefficient of the fin (57) and that of the absorbent.

Description

  The present invention relates to a heat exchanger, and particularly belongs to the technical field of a heat exchanger used in a humidity control apparatus that adjusts the humidity of air using an adsorbent and a refrigeration cycle.

  Conventionally, there has been one disclosed in Patent Document 1 as a heat exchanger having a function of adsorbing moisture in the air or releasing moisture into the air. This heat exchanger is provided with plate-like fins around a copper tube as a heat transfer tube, and adsorbent that adsorbs moisture in the air and desorbs moisture in the air on the copper tube and fin surfaces. Is carried.

  And this heat exchanger is used for the humidity control apparatus etc. which adjust humidity of air using an adsorption agent and a refrigerating cycle, for example as disclosed by the said patent document 1. FIG.

The humidity control apparatus includes two heat exchangers, and during operation, one of the two heat exchangers is supplied with a heating medium to the copper tube to become an evaporator, and the other is a refrigerant in the copper tube. Is supplied as a condenser. Further, by switching between the refrigerant and the heating medium supplied to each copper pipe, each heat exchanger functions alternately as an evaporator or as a condenser.
JP-A-7-265649

  By the way, the heat exchanger performs cooling and heating of the heat exchanger in order to repeat adsorption of moisture in the air and desorption of moisture in the air, as in the case of being used in the humidity control apparatus. Need to repeat. As a result, the constituent members of the heat exchanger such as the fins and the support layer repeat thermal expansion and contraction.

  Here, in general, the coefficient of linear thermal expansion of the member used for the fin of the heat exchanger and the coefficient of linear thermal expansion of the member used as the adsorbent or the support layer carrying the adsorbent are the respective materials. When the temperature change occurs in the heat exchanger, thermal stress is generated due to the difference in coefficient of linear thermal expansion between the support layer and the fin, and the adhesion surface between the support layer and the fin Acts as a shear stress. As a result, the carrier layer may be peeled off from the fins.

  The present invention has been made in view of the above points, and an object of the present invention is to improve the durability of the carrier layer by preventing the carrier layer and the fin from being separated from each other.

  The first invention is directed to a heat exchanger having a large number of fins (57) and an adsorbent for adsorbing moisture in the air and desorbing moisture in the air supported on the surface.

  The surface of the fin (57) is covered with a support layer (58) formed by blending the adsorbent and a binder for supporting the adsorbent on the surface of the fin (57).

  In addition, the carrier layer (58) has a weight blending ratio of the adsorbent and the binder of 5: 1 to 8: 1.

  The difference between the linear thermal expansion coefficient of the fin (57) and the linear thermal expansion coefficient of the support layer (58) is the difference between the linear thermal expansion coefficient of the fin (57) and the linear thermal expansion coefficient of the adsorbent. It shall be smaller than the difference.

  In the case of the above configuration, an adsorbent is supported on the surface of the fin (57), and when air to be treated passes near the fin (57), moisture in the air is adsorbed by the adsorbent and The air will be dehumidified. At this time, the heat of adsorption generated by the adsorption of moisture is recovered by the heat medium of the heat exchanger. On the other hand, when the heat is not recovered by the heat medium of the heat exchanger but is supplied by the heat medium, the adsorbent is heated and the water adsorbed on the adsorbent is desorbed. Thus, the air to be treated is humidified. That is, in order for the heat exchanger to repeat the adsorption of moisture in the air and the desorption of moisture into the air, the cooling and heating of the heat exchanger are repeated.

  Here, the adsorbent is supported on the surface of the fin (57) by the support layer (58) formed by mixing the adsorbent and the binder, and the surface of the fin (57) is the support layer (58). It is covered by. The binder bonds the adsorbents and fixes the adsorbent to the surface of the fin (57).

  In this case, generally, the linear thermal expansion coefficient of the member used as the adsorbent and the linear thermal expansion coefficient of the member used as the fin (57) of the heat exchanger are largely separated from each other, but the above-mentioned As described above, the binder is placed so that the linear thermal expansion coefficient of the support layer (58) in which the adsorbent and the binder are mixed is closer to the linear thermal expansion coefficient of the fin (57) than the linear thermal expansion coefficient of the adsorbent. A support layer (58) is formed by selection. For this reason, when the fin (57) thermally expands or contracts to generate thermal strain, the support layer (58) also expands or contracts in the same manner, and the thermal strain is close to the thermal strain of the fin (57). It becomes.

  In a second aspect based on the first aspect, the linear thermal expansion coefficient of the binder is greater than or equal to the linear thermal expansion coefficient of the fin (57).

  Generally, the linear thermal expansion coefficient of the member used as the adsorbent is smaller than the linear thermal expansion coefficient of the member used as the fin (57) of the heat exchanger (47, 49). In the case of the above configuration, the adsorbent is blended with a binder having a linear thermal expansion coefficient larger than the linear thermal expansion coefficient of the fin (57), whereby the linear thermal expansion coefficient of the support layer (58) is set to the fin (57). It is close to the linear thermal expansion coefficient.

  The linear thermal expansion coefficient of the carrier layer (58) largely depends on the weight ratio of the adsorbent and the binder and the respective linear thermal expansion coefficients. In the present invention, attention is paid to the linear thermal expansion coefficient, and the binder is selected so that the linear thermal expansion coefficient increases in the order of the adsorbent, the fin (57), and the binder. The weight ratio between the adsorbent and the binder to be blended is determined by the adsorptivity and adhesion required for the support layer (58).

  In a third aspect based on the first aspect, the binder is an organic water-based emulsion binder.

  In the case of the above configuration, the organic water emulsion binder is excellent in flexibility as compared with the inorganic binder.

A fourth invention, in the third invention, the aqueous emulsion binders, urethane resin, you shall an acrylic resin or an ethylene-vinyl acetate copolymer.

  According to the present invention, the difference between the linear thermal expansion coefficient of the fin (57) and the linear thermal expansion coefficient of the support layer (58) is obtained by calculating the linear thermal expansion coefficient of the fin (57) and the linear heat of the adsorbent. By making it smaller than the difference from the expansion coefficient, the linear thermal expansion coefficient of the support layer (58) is brought close to the linear thermal expansion coefficient of the fin (57). As a result, even if the fin (57) repeats thermal expansion and contraction due to heating and cooling, the support layer (58) can follow the thermal expansion and contraction of the fin (57), and the bonding surface of both It is possible to reduce the shear stress generated in As a result, the carrier layer (58) and the fins (57) can be prevented from being peeled off, and the durability of the carrier layer (58) can be improved.

  Moreover, it is preferable that the linear thermal expansion coefficient of the support layer (58) is substantially equal to the linear thermal expansion coefficient of the fin (57). In such a case, the thermal strain of the support layer (58) and the thermal strain of the fin (57) are substantially equal, and almost no shear stress is generated on the bonding surface between them.

  According to the second aspect of the invention, in addition to the first aspect of the invention, in addition to the linear thermal expansion coefficient of the fin (57), the linear thermal expansion coefficient of the binder is set to be equal to or higher than the linear thermal expansion coefficient of the fin (57). The coefficient can be made closer to the linear thermal expansion coefficient of the fin (57) more effectively.

According to the third invention, since the organic water emulsion binder is adopted, it is more flexible than the inorganic binder, strong against sudden temperature changes and impacts, and difficult to peel off, and good adhesion. Can be obtained. Therefore, when the linear thermal expansion coefficient of the fin (57) and the linear thermal expansion coefficient of the support layer (58) do not completely match, the thermal stress generated thereby is caused by the flexibility of the support layer (58) itself. It can be absorbed by sex. As a result, in addition to the effects of the first invention, the followability of the support layer (58) to the thermal expansion and contraction of the fins (57) is further improved, and the durability of the support layer (58) is further improved. It is Ru can.

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

<< Embodiment of the Invention >>
-Configuration of humidity control device-
<About the entire device>
FIG. 1 schematically shows a configuration of a humidity control apparatus including a heat exchanger according to an embodiment of the present invention. FIG. 1A is a cross-sectional view taken along line XX in FIG. ) Is a plan view showing the inside, and the lower side is the front side in the figure. FIG.1 (c) is sectional drawing in the YY line of FIG.1 (b). This humidity control device includes a rectangular box-shaped casing (1), and the inside of the casing (1) is a first partition plate (3) extending in the front-rear direction and a left first space (5) having a large storage volume, and a storage volume. Is divided into a small second space (7) on the right side. The first space (5) includes a central third space (13) having a large storage volume by two front and rear second and third partition plates (9, 11) extending parallel to the left and right, and a storage volume. The third space (13) is divided into a small front and rear two fourth and fifth spaces (15, 17). ) And is divided. Further, the rear fifth space (17) is partitioned vertically by a fifth partition plate (21) extending horizontally from side to side, the upper space is defined as the first inflow passage (23), and the lower space is defined as the first space. Outflow channel (25). On the other hand, the fourth space (15) on the front side is also divided vertically by a sixth partition plate (27) extending horizontally from side to side, the upper space is the second inlet channel (29), and the lower space is the second outlet. Road (31).

  The third partition plate (11) has four first to fourth openings (11a to 11d), the left and right spaces (13a, 13b) of the third space (13), the first inflow passage (23), and the first It is formed side by side vertically and horizontally so as to communicate with the outflow path (25) (see FIG. 1 (a)). Also, the second partition plate (9) has four fifth to eighth openings (9a to 9d), the left and right spaces (13a, 13b) of the third space (13), the second inflow channel (29), and It is formed side by side vertically and horizontally so as to communicate with the second outflow path (31) (see FIG. 1C). Although not shown, dampers are provided in the first to fourth openings (11a to 11d) and the fifth to eighth openings (9a to 9d) so as to be freely opened and closed.

  An outdoor air suction port (33) is formed on the rear side of the left side surface of the casing (1) so as to communicate with the first inflow passage (23), and on the rear side of the right side surface of the casing (1). An exhaust outlet (35) is formed, and the exhaust outlet (35) is connected to an exhaust fan (37) disposed on the rear side of the second space (7) and communicates with the first outflow passage (25). ing. On the other hand, an indoor air suction port (39) is formed on the front side of the left side surface of the casing (1) so as to communicate with the second inflow passage (29), and an air supply port is provided on the front side of the right side surface of the casing (1). An air outlet (41) is formed, and the air supply outlet (41) is connected to an air supply fan (43) disposed on the front side of the second space (7) and communicates with the second outflow passage (31). ing.

  In the casing (1) thus configured, a refrigerant circuit (45) as shown in FIG. 2 is accommodated. The refrigerant circuit (45) includes a first heat exchanger (47), a second heat exchanger (49), a compressor (51), a four-way switching valve (53), and an electric expansion valve (55). A closed circuit is filled with a refrigerant, and a vapor compression refrigeration cycle is performed by circulating the refrigerant. Specifically, the discharge side of the compressor (51) is connected to the first port of the four-way switching valve (53), and the suction side is connected to the second port of the four-way switching valve (53). One end of the first heat exchanger (47) is connected to the third port of the four-way switching valve (53), and the other end is connected to one end of the second heat exchanger (49) via the electric expansion valve (55). ing. The other end of the second heat exchanger (49) is connected to the fourth port of the four-way switching valve (53). In the four-way switching valve (53), the first port and the third port communicate with each other, the second port and the fourth port communicate with each other (the state shown in FIG. 2A), and the first port and the fourth port communicate with each other. It is configured to be able to switch to a state where the second port and the third port communicate with each other (the state shown in FIG. 2B). In the refrigerant circuit (45), the first heat exchanger (47) functions as a condenser and the second heat exchanger (49) functions as an evaporator by switching the four-way switching valve (53). The first refrigeration cycle operation and the second refrigeration cycle operation in which the first heat exchanger (47) functions as an evaporator and the second heat exchanger (49) functions as a condenser are switched and performed. ing. In addition, as shown in FIG. 1, each component of the refrigerant circuit (45) includes a first heat exchanger (47) in the right space (13b) of the third space (13) and a second heat exchanger (49 ) Is disposed in the left space (13a) of the third space (13), and the compressor (51) is disposed in the middle of the second space (7). Although not shown, a four-way switching valve (53) and an electric expansion valve (55) are also arranged in the second space (7).

《About heat exchanger》
The first and second heat exchangers (47, 49) are both cross fin type fin-and-tube heat exchangers as shown in FIG. 3, and a plurality of aluminum alloy fins (57) are spaced apart. A fin group (59) arranged in parallel with a gap is provided. The fin array direction both ends of the fin group (59) and the end faces on both ends of the fin longitudinal direction are surrounded by a rectangular metal frame plate (61), and the first and second heat exchangers (47, 49) are Arranged in the left and right spaces (13a, 13b) of the third space (13) via the frame plate (61). A heat transfer tube (63) is disposed in the fin group (59). The heat transfer tube (63) is formed in a meandering manner with a straight tube portion (63a) and a U-shaped tube portion (63b), and the straight tube portion (63a) penetrates the fin group (59) in the fin arrangement direction. In addition, the U-shaped tube portion (63b) protrudes from the frame plate (61). One end of the connection pipe (65) is connected to one end of the heat transfer pipe (63), and the connection pipe (65) connects the heat transfer pipe (63) to a refrigerant pipe (not shown).

As a feature of the present invention, the surfaces of the fins (57) of the first and second heat exchangers (47, 49) are covered with a support layer (58) made of an adsorbent and a binder. Zeolite is used as the adsorbent, and urethane resin is used as the binder. Here, the linear thermal expansion coefficient of each material is 23.6 × 10 ⁻⁶ [K ⁻¹ ] for the aluminum alloy that is the material of the fin (57), and 4.5 to 6.1 × 10 ⁻⁶ [K ⁻¹ ] for zeolite. The urethane resin is 100 to 200 × 10 ⁻⁶ [K ⁻¹ ]. And the support layer (58) is a state in which zeolite and urethane resin are blended at a weight ratio of 5: 1 to 8: 1, and the adsorbent, the fin (57), and the adsorbent are fixed to each other by a binder. It is laminated on the fin (57).

  Since the fin (57) and the adsorbent (zeolite) have large linear thermal expansion coefficients, when the heat exchanger (47, 49) is heated or cooled, the thermal strains of the fin (57) and the adsorbent (zeolite) are greatly different. If the adsorbent is supported on the surface of the fin (57) by a binder having a linear thermal expansion coefficient substantially the same as or lower than that of the adsorbent, the thermal stress due to the difference in the linear thermal expansion coefficient between the two is Shear stress is generated at the interface between the carrier layer (58) and the fin (57). This shear stress is particularly large, for example, around the edge of the fin (57) and around the hole, and is one of the major factors that cause the carrier layer (58) to peel from the fin (57).

  Therefore, the linear thermal expansion coefficient of the binder interposed between the adsorbent and the fin (57) and between the adsorbent and the adsorbent is made larger than that of the fin (57) material, that is, the fin (57) material. The binder is selected so that the linear thermal expansion coefficient of the resin becomes a value between the linear thermal expansion coefficient of the adsorbent and the linear thermal expansion coefficient of the binder.

  By doing so, the linear thermal expansion coefficient of the entire support layer (58) is brought closer to the linear thermal expansion coefficient of the fins (57) than in the case of the adsorbent alone. That is, when the fin (57) expands or contracts by heating or cooling, the adsorbent having a relatively smaller linear thermal expansion coefficient than the fin (57) does not cause thermal distortion as much as the fin (57). A binder that is interposed between the adsorbent and the like and has a relatively higher linear thermal expansion coefficient than the fin (57) causes thermal strain more than that of the fin (57). As described above, the binder compensates for the thermal strain of the adsorbent, whereby the entire support layer (58) can follow the thermal expansion or contraction of the fin (57).

  In addition, since a urethane resin belonging to an organic water-based emulsion binder is employed as a binder, it is superior in flexibility to an inorganic binder and cannot completely follow the thermal expansion and contraction of the fin (57). Even if it is a case, the thermal stress generated by it can be absorbed by the flexibility of the urethane resin.

  That is, the followability of the carrier layer (58) to the thermal expansion or contraction of the fin is such that the linear thermal expansion coefficient of the carrier layer (58) is brought close to the linear thermal expansion coefficient of the fin (57) by the aqueous emulsion binder, and the aqueous system It is improved by the flexibility of the emulsion binder itself.

  In addition, after carrying out surface treatment of the surface of a fin (57), the said support layer (58) apply | coats the slurry which mixed adsorbent and binder solution on the surface of a fin (57), and a slurry solidifies by drying and solidifies. The agent, the fin (57), and the adsorbent are fixed by a binder. As the surface treatment, a degreasing treatment or the like for preventing the slurry from repelling on the surface of the fin (57) is performed.

  In addition, the heat exchanger (47, 49) has a support layer (58) laminated not only on the surface of the fin (57) but also on the heat transfer pipe (63), the connecting pipe (65) and the frame plate (61). The adsorption performance of the heat exchanger (47, 49) as a whole is improved.

  The humidity control operation of the humidity control apparatus configured as described above will be described with reference to FIGS.

-Humidity control operation of humidity control device-
In this humidity control apparatus, the dehumidifying operation and the humidifying operation can be switched. Further, during the dehumidifying operation and the humidifying operation, the first operation and the second operation are alternately repeated.

《Dehumidification operation》
In the dehumidifying operation, the air supply fan (43) and the exhaust fan (37) are operated in the humidity control apparatus. The humidity control apparatus takes in outdoor air (OA) as first air and supplies it to the room, while taking in indoor air (RA) as second air and discharges it to the outside.

  First, the first operation during the dehumidifying operation will be described with reference to FIGS. In the first operation, the adsorbent is regenerated in the first heat exchanger (47), and the outdoor air (OA), which is the first air, is dehumidified in the second heat exchanger (49).

  During the first operation, in the refrigerant circuit (45), the four-way switching valve (53) is switched to the state shown in FIG. When the compressor (51) is operated in this state, the refrigerant circulates in the refrigerant circuit (45), the first heat exchanger (47) becomes a condenser, and the second heat exchanger (49) becomes an evaporator. A first refrigeration cycle operation is performed. Specifically, the refrigerant discharged from the compressor (51) dissipates heat and condenses in the first heat exchanger (47), and then is sent to the electric expansion valve (55) to be depressurized. The decompressed refrigerant absorbs heat and evaporates in the second heat exchanger (49), and is then sucked into the compressor (51) and compressed. Then, the compressed refrigerant is discharged again from the compressor (51).

  In the first operation, the second opening (11b), the third opening (11c), the fifth opening (9a), and the eighth opening (9d) are in the open state, and the first opening (11a) and the fourth opening ( 11d), the sixth opening (9b) and the seventh opening (9c) are closed. Then, as shown in FIG. 4, indoor air (RA) as second air is supplied to the first heat exchanger (47), and outdoor air (OA) as the first air is supplied to the second heat exchanger (49). ) Is supplied.

  Specifically, the second air flowing in from the indoor air inlet (39) passes through the fifth inlet (9a) from the second inlet (29) to the right space (13b) of the third space (13). It is sent. In the right space (13b), the second air passes through the first heat exchanger (47) from top to bottom. In the first heat exchanger (47), the adsorbent supported on the fin (57) surface is heated by the refrigerant, and moisture is desorbed from the adsorbent. The moisture desorbed from the adsorbent is given to the second air passing through the first heat exchanger (47). The second air given moisture in the first heat exchanger (47) flows out from the right space (13b) of the third space (13) through the third opening (11c) to the first outflow passage (25). To do. Thereafter, the second air is sucked into the exhaust fan (37), and discharged from the exhaust outlet (35) to the outside as exhaust air (EA).

  On the other hand, the 1st air which flowed in from the outdoor air suction inlet (33) is sent into the left side space (13a) of the 3rd space (13) through the 2nd opening (11b) from the 1st inflow path (23). In the left space (13a), the first air passes through the second heat exchanger (49) from top to bottom. In the second heat exchanger (49), the moisture in the first air is adsorbed by the adsorbent carried on the surface of the fin (57). The heat of adsorption generated at that time is absorbed by the refrigerant. The first air dehumidified by the second heat exchanger (49) flows out from the left space (13a) of the third space (13) through the eighth opening (9d) to the second outlet channel (31). Thereafter, the first air is sucked into the air supply fan (43), and is supplied into the room as supply air (SA) from the air supply outlet (41).

  Next, the second operation during the dehumidifying operation will be described with reference to FIGS. In the second operation, the adsorbent is regenerated in the second heat exchanger (49), and the outdoor air (OA) that is the first air is dehumidified in the first heat exchanger (47).

  During the second operation, in the refrigerant circuit (45), the four-way switching valve (53) is switched to the state shown in FIG. When the compressor (51) is operated in this state, the refrigerant circulates in the refrigerant circuit (45), the first heat exchanger (47) becomes an evaporator, and the second heat exchanger (49) becomes a condenser. A second refrigeration cycle operation is performed. Specifically, the refrigerant discharged from the compressor (51) dissipates heat and condenses in the second heat exchanger (49), and then is sent to the electric expansion valve (55) to be depressurized. The decompressed refrigerant absorbs heat and evaporates in the first heat exchanger (47), and then is sucked into the compressor (51) and compressed. Then, the compressed refrigerant is discharged again from the compressor (51).

  In the second operation, the first opening (11a), the fourth opening (11d), the sixth opening (9b), and the seventh opening (9c) are in the open state, and the second opening (11b) and the third opening ( 11c), the fifth opening (9a) and the eighth opening (9d) are closed. Then, as shown in FIG. 5, outdoor air (OA) as first air is supplied to the first heat exchanger (47), and indoor air (RA) as second air is supplied to the second heat exchanger (49). ) Is supplied.

  Specifically, the second air flowing in from the indoor air inlet (39) passes through the sixth opening (9b) from the second inlet (29) to the left space (13a) of the third space (13). It is sent. In the left space (13a), the second air passes through the second heat exchanger (49) from top to bottom. In the second heat exchanger (49), the adsorbent supported on the surface of the fin (57) is heated by the refrigerant, and moisture is desorbed from the adsorbent. The moisture desorbed from the adsorbent is given to the second air passing through the second heat exchanger (49). The second air given moisture in the second heat exchanger (49) flows out from the left space (13a) of the third space (13) through the fourth opening (11d) to the first outflow passage (25). To do. Thereafter, the second air is sucked into the exhaust fan (37), and discharged from the exhaust outlet (35) to the outside as exhaust air (EA).

  On the other hand, the 1st air which flowed in from the outdoor air suction inlet (33) is sent into the right side space (13b) of the 3rd space (13) through the 1st opening (11a) from the 1st inflow passage (23). In the right space (13b), the first air passes through the first heat exchanger (47) from top to bottom. In the first heat exchanger (47), the moisture in the first air is adsorbed by the adsorbent carried on the surface of the fin (57). The heat of adsorption generated at that time is absorbed by the refrigerant. The first air dehumidified by the first heat exchanger (47) flows out from the right space (13b) of the third space (13) through the seventh opening (9c) to the second outflow passage (31). Thereafter, the first air is sucked into the air supply fan (43), and is supplied into the room as supply air (SA) from the air supply outlet (41).

《Humidification operation》
During the humidifying operation, the air supply fan (43) and the exhaust fan (37) are operated in the humidity control apparatus. The humidity control apparatus takes in indoor air (RA) as first air and discharges it outside the room, while taking in outdoor air (OA) as second air and supplies it to the room.

  First, the first operation during the humidifying operation will be described with reference to FIGS. 2 and 6. In this first operation, the outdoor air (OA) that is the second air is humidified in the first heat exchanger (47), and the indoor air (RA) that is the first air in the second heat exchanger (49). Water is collected from the water.

  During the first operation, in the refrigerant circuit (45), the four-way switching valve (53) is switched to the state shown in FIG. When the compressor (51) is operated in this state, the refrigerant circulates in the refrigerant circuit (45), the first heat exchanger (47) becomes a condenser, and the second heat exchanger (49) becomes an evaporator. A first refrigeration cycle operation is performed.

  In the first operation, the first opening (11a), the fourth opening (11d), the sixth opening (9b), and the seventh opening (9c) are in the open state, and the second opening (11b) and the third opening (11c), the fifth opening (9a) and the eighth opening (9d) are closed. Then, as shown in FIG. 6, outdoor air (OA) as second air is supplied to the first heat exchanger (47), and indoor air as first air is supplied to the second heat exchanger (49). (RA) is supplied.

  Specifically, the 1st air which flowed in from the indoor air suction inlet (39) passes through the 6th opening (9b) from the 2nd inflow path (29) to the left space (13a) of the 3rd space (13). It is sent. In the second heat exchange chamber (42), the first air passes through the second heat exchanger (49) from top to bottom. In the left space (13a), the moisture in the first air is adsorbed by the adsorbent carried on the surface of the fin (57). The heat of adsorption generated at that time is absorbed by the refrigerant. Thereafter, the first air deprived of moisture passes through the fourth opening (11d), the first outflow passage (25), and the exhaust fan (37) in this order, and from the exhaust outlet (35) as exhaust air (EA). It is discharged outside the room.

  On the other hand, the 2nd air which flowed in from the outdoor air suction inlet (33) is sent into the right space (13b) of the 3rd space (13) through the 1st opening (11a) from the 1st inflow passage (23). In the right space (13b), the second air passes through the first heat exchanger (47) from top to bottom. In the first heat exchanger (47), the adsorbent supported on the fin (57) surface is heated by the refrigerant, and moisture is desorbed from the adsorbent. The moisture desorbed from the adsorbent is given to the second air passing through the first heat exchanger (47). Thereafter, the humidified second air sequentially passes through the seventh opening (9c), the second outflow passage (31), and the air supply fan (43), and serves as supply air (SA) from the air supply outlet (41). Supplied indoors.

  Next, the second operation during the humidifying operation will be described with reference to FIGS. In the second operation, the outdoor air (OA) that is the second air is humidified in the second heat exchanger (49), and the indoor air (RA) that is the first air in the first heat exchanger (47). Water is collected from the water.

  During the second operation, in the refrigerant circuit (45), the four-way switching valve (53) is switched to the state shown in FIG. When the compressor (51) is operated in this state, the refrigerant circulates in the refrigerant circuit (45), the first heat exchanger (47) becomes an evaporator, and the second heat exchanger (49) becomes a condenser. A second refrigeration cycle operation is performed.

  In the second operation, the second opening (11b), the third opening (11c), the fifth opening (9a), and the eighth opening (9d) are in the open state, and the first opening (11a) and the fourth opening (11d), the sixth opening (9b) and the seventh opening (9c) are closed. Then, as shown in FIG. 7, indoor air (RA) as first air is supplied to the first heat exchanger (47), and outdoor air as second air is supplied to the second heat exchanger (49). (OA) is supplied.

  Specifically, the 1st air which flowed in from the indoor air suction inlet (39) passes through the 5th opening (9a) from the 2nd inflow path (29) to the right space (13b) of the 3rd space (13). It is sent. In the right space (13b), the first air passes through the first heat exchanger (47) from top to bottom. In the first heat exchanger (47), the moisture in the first air is adsorbed by the adsorbent carried on the surface of the fin (57). The heat of adsorption generated at that time is absorbed by the refrigerant. Thereafter, the first air deprived of moisture passes through the third opening (11c), the first outflow passage (25), and the exhaust fan (37) in this order, and from the exhaust outlet (35) as exhaust air (EA). It is discharged outside the room.

  On the other hand, the 2nd air which flowed in from the outdoor air suction inlet (33) is sent into the left side space (13a) of the 3rd space (13) through the 2nd opening (11b) from the 1st inflow path (23). In the left space (13a), the second air passes through the second heat exchanger (49) from top to bottom. In the second heat exchanger (49), the adsorbent supported on the surface of the fin (57) is heated by the refrigerant, and moisture is desorbed from the adsorbent. The moisture desorbed from the adsorbent is given to the second air passing through the second heat exchanger (49). Thereafter, the humidified second air sequentially passes through the eighth opening (9d), the second outlet channel (31), and the air supply fan (43), and is supplied as supply air (SA) from the air supply outlet (41). Supplied indoors.

  As described above, the dehumidifying operation and the humidifying operation in the full ventilation mode have been described. This humidity control apparatus takes in indoor air (RA) as the first air and supplies it into the room, while taking in outdoor air (OA) as the second air. Dehumidifying operation in circulation mode for discharging outside, humidifying operation in circulation mode for taking in outdoor air (OA) as first air, and discharging indoor air (RA) as second air into the room, While taking outdoor air (OA) as the first air and supplying it into the room, while taking outdoor air (OA) as the second air and taking it out of the room, dehumidifying operation in the air supply mode, and outdoor air (OA) as the first air While exhausting outside the intake chamber, humidification operation in the air supply mode for supplying outdoor air (OA) as the second air into the indoor chamber, and supplying the indoor air (RA) as the first air into the indoor chamber, Dehumidifying operation in exhaust mode in which air (RA) is taken in as second air and discharged outside the room, while indoor air (RA) is taken in as first air and discharged outside the room, while room air (RA) is taken in as second air in the room The humidification operation in the exhaust mode to be supplied to is also performed.

-Effects of this embodiment-
In the humidity control operation, the first heat exchanger (47) and the second heat exchanger (49) are repeatedly heated and cooled by the refrigerant, and the fin (57) repeats thermal expansion and contraction. The support layer (58) laminated on the surface of the fin (57) can follow the expansion and contraction of the fin (57) without peeling from the fin (57).

  Specifically, since the linear thermal expansion coefficient of the support layer (58) is close to the linear thermal expansion coefficient of the fin (57), the thermal expansion and contraction of the fin (57) follows and the thermal expansion is similarly performed. And shrink. As a result, it is possible to reduce the thermal stress generated between them, prevent the carrier layer (58) from peeling off, and improve the durability of the carrier layer (58). The linear thermal expansion coefficient of the support layer (58) is preferably substantially equal to the linear thermal expansion coefficient of the fin (57), and the followability improves as the difference between the two is smaller.

  And, urethane resin is used as the binder, and the linear thermal expansion coefficient of this urethane resin is larger than the linear thermal expansion coefficient of the aluminum alloy that is the fin material. 57) can be effectively brought close to the linear thermal expansion coefficient.

  Further, this urethane resin belongs to an organic aqueous emulsion binder, and by adopting an organic aqueous emulsion binder, the support layer (58) is more flexible than an inorganic binder, and has a sharp effect. It is strong against temperature changes and impacts and hardly peels off, and good adhesion can be obtained. For this reason, the linear thermal expansion coefficient of the support layer (58) and the linear thermal expansion coefficient of the fin (57) are close to each other, but do not completely coincide with each other, and the difference between the support layer (58) and the support layer (58) Even when thermal stress is generated at the interface with the fin (57), the carrier layer (58) absorbs the thermal stress by the flexibility of the carrier layer (58) itself and peels off from the fin (57). hard. Therefore, the durability of the carrier layer (58) can be further improved.

<< Other Embodiments >>
The present invention may be configured as follows with respect to the above embodiment. That is, zeolite is used as the adsorbent, but other adsorbents may be used, such as silica gel, a mixture of zeolite and silica gel, activated carbon, hydrophilic or water-absorbing organic polymer polymer material, carboxyl Excels in adsorbing moisture, such as ion exchange resin-based materials having functional groups or sulfonic acid groups, functional polymer materials such as thermosensitive polymers, or clay mineral materials such as sepiolite, imogolite, allophane or kaolinite Anything can be used.

  In addition to the urethane resin, for example, an acrylic resin or an ethylene vinyl acetate copolymer can be used for the binder. These are excellent in flexibility, can follow the thermal expansion and contraction of the fin (57), and are blended with the adsorbent to form the support layer (58), thereby forming the linear heat of the support layer (58). The expansion coefficient can be brought close to the linear thermal expansion coefficient of the fin (57).

  The present invention is useful for a humidity control apparatus that adjusts the humidity of air using an adsorbent and a refrigeration cycle.

It is a schematic block diagram of the humidity control apparatus which concerns on embodiment. It is a piping system diagram showing a refrigerant circuit of a humidity control apparatus according to an embodiment. It is a schematic block diagram of the heat exchanger which concerns on embodiment. It is a schematic block diagram of the humidity control apparatus which shows the flow of the air in the 1st operation | movement of a dehumidification driving | operation. It is a schematic block diagram of the humidity control apparatus which shows the flow of the air in 2nd operation | movement of a dehumidification driving | operation. It is a schematic block diagram of the humidity control apparatus which shows the flow of the air in the 1st operation | movement of a humidification driving | operation. It is a schematic block diagram of the humidity control apparatus which shows the flow of the air in 2nd operation | movement of a humidification driving | operation.

Explanation of symbols

47 1st heat exchanger (heat exchanger)
49 2nd heat exchanger (heat exchanger)
57 Fin 58 Carrier Layer

Claims (4)

A heat exchanger having a large number of fins (57) and an adsorbent for adsorbing moisture in the air and desorbing moisture in the air supported on the surface,
The surface of the fin (57) is covered with a support layer (58) formed by blending the adsorbent and a binder for supporting the adsorbent on the surface of the fin (57),
The carrier layer (58) has a weight blending ratio of the adsorbent and the binder of 5: 1 to 8: 1,
The difference between the linear thermal expansion coefficient of the fin (57) and the linear thermal expansion coefficient of the support layer (58) is based on the difference between the linear thermal expansion coefficient of the fin (57) and the linear thermal expansion coefficient of the adsorbent. Is a small heat exchanger. The heat exchanger according to claim 1,
The heat exchanger according to claim 1, wherein a linear thermal expansion coefficient of the binder is equal to or greater than a linear thermal expansion coefficient of the fin (57). The heat exchanger according to claim 1,
The heat exchanger according to claim 1, wherein the binder is an organic water-based emulsion binder. The heat exchanger according to claim 3,
The heat exchanger according to claim 1, wherein the aqueous emulsion binder is a urethane resin, an acrylic resin, or an ethylene vinyl acetate copolymer.

Images