JP6878698B2 - Heat exchanger and refrigeration cycle equipment - Google Patents

Description

The present invention, the heat exchanger and related to the refrigeration cycle equipment, in particular, relates to a heat exchanger adsorbent is applied, and the refrigeration cycle apparatus provided with such a heat exchanger.

Conventionally, heat exchangers in which an adsorbent that adsorbs moisture (moisture, water vapor) in the air is applied (supported) on the surface of fins have been known. For example, Patent Document 1 proposes a refrigerator in which an adsorbent containing an adhesive and having a water-absorbing action is adhered to the surfaces of fins and heat transfer tubes.

The adsorbent used in this type of heat exchanger basically has the property that the amount of water adsorbed increases as the temperature of the adsorbent decreases, and the amount of water adsorbed decreases as the temperature of the adsorbent increases. Has. Further, when the adsorbent absorbs water, heat is generated and the temperature of the adsorbent rises. Therefore, in order to increase the amount of water adsorbed per unit time, it is necessary to efficiently cool the adsorbent. In the heat exchanger disclosed in Patent Document 1, in order to efficiently cool the adsorbent, the adsorbent is thickly applied to the fin portion near the heat transfer tube, and the adsorbent is applied to the fin portion far from the heat transfer tube. Is applied thinly.

Jikkai Sho 63-142695

However, the conventional heat exchanger has the following problems. When the heat exchanger is operated, air is sent to the heat exchanger, air flows between the fins through which the heat transfer tube is inserted, and heat is exchanged between the refrigerant and the like flowing through the heat transfer tube and the air. Is done. At this time, the wind speed flowing through the fin portion located on the leeward side of the heat transfer tube is smaller than the wind speed flowing through the fin portion located on the windward side of the heat transfer tube.

Therefore, if the amount of the adsorbent applied to the fin portion located on the leeward side of the heat transfer tube is large, the amount of the adsorbent is excessive with respect to the amount of water (moisture content, water vapor amount) sent by the flowing air. become. As a result, the production cost of the heat exchanger will increase accordingly.

The present invention has been made to solve the above problems, one purpose is to provide a heat exchanger that can contribute to reduction of production cost, and the other purpose is to provide such heat exchange. to provide a refrigeration cycle apparatus having a vessel.

The heat exchanger according to the present invention includes a first fin, a first heat transfer tube, and a first adsorbent. The first fin has a first end portion and a second end portion facing each other with a distance in the first direction, and extends in a second direction intersecting the first direction. The first heat transfer tube is inserted into a portion of the first fin located between the first end portion and the second end portion. The first adsorbent is formed on the first fin. The first adsorbent includes a first part of the first adsorbent and a second part of the first adsorbent. The first part of the first adsorbent is formed in the first part of the first fin extending from the first end part to the first heat transfer tube. The second part of the first adsorbent is formed in the second part of the first fin from the first heat transfer tube to the second end part. The thickness of the second part of the first adsorbent is thinner than the thickness of the first part of the first adsorbent. In the first fin, the first end is located on the leeward side and the second end is located on the leeward side. The second portion of the first fin is located in the leeward region of the first heat transfer tube.

The refrigeration cycle device according to the present invention is a refrigeration cycle device provided with the above-mentioned heat exchanger.

According to the heat exchanger according to the present invention, the first adsorbent formed on the first fin is the first adsorbent formed on the first portion of the first fin from the first end portion to the first heat transfer tube. The thickness of the second part of the first adsorbent, which includes the first part of the agent and the second part of the first adsorbent formed in the second part of the first fin from the first heat transfer tube to the second end. Is thinner than the thickness of the first part of the first adsorbent. As a result, in the portion of the first fin located on the leeward side where the amount of moisture sent from the air is smaller than that on the windward side, the second part of the first adsorbent corresponding to the small amount of moisture is formed. Become. As a result, the cost due to excessive application of the first adsorbent can be suppressed, which can contribute to the reduction of the production cost.

According to the refrigeration cycle apparatus according to the present invention, it is possible to contribute to the reduction of production cost by applying the above-mentioned heat exchanger.

It is a figure which shows an example of the refrigerant circuit of the refrigerating cycle apparatus to which the heat exchanger according to each embodiment is applied. It is a perspective view of the heat exchanger which concerns on each embodiment. FIG. 5 is a partial plan view showing fins coated with an adsorbent in the heat exchanger according to the first embodiment. In the same embodiment, it is a cross-sectional view taken along the cross-sectional line IV-IV shown in FIG. In the same embodiment, it is a cross-sectional view taken along the cross-sectional line VV shown in FIG. It is a partial plan view which shows the fin coated with the adsorbent in the heat exchanger which concerns on a comparative example. It is sectional drawing in sectional line VII-VII shown in FIG. It is sectional drawing in sectional line VIII-VIII shown in FIG. FIG. 5 is a partial plan view showing fins coated with an adsorbent in the heat exchanger according to the second embodiment. In the same embodiment, it is a cross-sectional view taken along the cross-sectional line XX shown in FIG. In the same embodiment, it is sectional drawing in sectional line XI-XI shown in FIG. In the same embodiment, it is a partial plan view which shows the fin before the adsorbent is applied. In the same embodiment, it is sectional drawing in sectional line XIII-XIII shown in FIG. It is a perspective view of the heat exchanger according to the third embodiment. In the same embodiment, it is a partial plan view which shows the fin to which the adsorbent is applied. In the same embodiment, it is sectional drawing in sectional line XVI-XVI shown in FIG. In the same embodiment, it is sectional drawing in sectional line XVII-XVII shown in FIG. It is a perspective view which shows one step of the manufacturing method of the heat exchanger which concerns on Embodiment 4. FIG. It is a perspective view which shows the process performed after the process shown in FIG. 18 in the same embodiment. It is a perspective view which shows the process performed after the process shown in FIG. 19 in the same embodiment. In the same embodiment, it is a partial plan view which shows the fin to which the adsorbent is applied. In the same embodiment, it is sectional drawing in sectional line XXII-XXII shown in FIG. In the same embodiment, it is sectional drawing in sectional line XXIII-XXIII shown in FIG. In each embodiment, it is a partial plan view showing fins coated with an adsorbent in the heat exchanger according to the modified example. It is sectional drawing in sectional line XXV-XXV shown in FIG. In each embodiment, it is a partial plan view showing fins coated with an adsorbent in the heat exchanger according to another modification. FIG. 6 is a cross-sectional view taken along the cross-sectional line XXVII-XXVII shown in FIG.

First, an example of a refrigeration cycle apparatus to which the heat exchanger according to each embodiment is applied will be described. As shown in FIG. 1, the refrigeration cycle device 1 includes a compressor 3, an indoor heat exchanger 5, an indoor fan 7, an expansion valve 9, an outdoor heat exchanger 11, an outdoor fan 13, and a four-way valve 15. The compressor 3, the indoor heat exchanger 5, the expansion valve 9, the outdoor heat exchanger 11 and the four-way valve 15 are connected by a refrigerant pipe 17.

The outdoor heat exchanger 11 will be described as an example of the heat exchanger according to each embodiment. As shown in FIG. 2, in the heat exchanger 21 as the outdoor heat exchanger 11, a plurality of fins 23 are arranged at intervals from each other as the first fin or the second fin, and penetrate the plurality of fins 23. As described above, the heat transfer tube 27 as the first heat transfer tube or the second heat transfer tube is inserted. The heat transfer tubes 27 are arranged so as to be spaced apart from each other in the direction in which the fins 23 extend. As will be described later, the surface of each fin 23 is coated with an adsorbent as a first adsorbent or a second adsorbent that adsorbs moisture (moisture, water vapor) in the air. In this specification, the adsorbent will be specifically described later, assuming that the adsorbent includes an adhesive.

Next, as the operation of the refrigeration cycle device 1 described above, first, the case of the heating operation will be described. By driving the compressor 3, a high-temperature and high-pressure gas refrigerant is discharged from the compressor 3. The discharged high-temperature and high-pressure gas refrigerant (single-phase) flows into the indoor heat exchanger 5 via the four-way valve 15. In the indoor heat exchanger 5, heat exchange is performed between the gas refrigerant that has flowed in and the air supplied by the indoor fan 7. The high-temperature and high-pressure gas refrigerant condenses into a high-pressure liquid refrigerant (single-phase). This heat exchange heats the room. The high-pressure liquid refrigerant sent out from the indoor heat exchanger 5 becomes a two-phase state refrigerant of a low-pressure gas refrigerant and a liquid refrigerant by the expansion valve 9.

The two-phase refrigerant flows into the outdoor heat exchanger 11. The outdoor heat exchanger 11 functions as an evaporator. In the outdoor heat exchanger 11, heat exchange is performed between the flowing two-phase refrigerant and the air supplied by the outdoor fan 13. Of the two-phase refrigerants, the liquid refrigerant evaporates to become a low-pressure gas refrigerant (single-phase). The low-pressure gas refrigerant sent out from the outdoor heat exchanger 11 flows into the compressor 3 via the four-way valve 15. The low-pressure gas refrigerant that has flowed into the compressor 3 is compressed to become a high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 3 again. Hereinafter, this cycle is repeated.

Next, the case of cooling operation will be described. By driving the compressor 3, a high-temperature and high-pressure gas refrigerant is discharged from the compressor 3. The discharged high-temperature and high-pressure gas refrigerant (single-phase) flows into the outdoor heat exchanger 11 via the four-way valve 15. The outdoor heat exchanger 11 functions as a condenser. In the outdoor heat exchanger 11, heat exchange is performed between the flowing refrigerant and the air supplied by the outdoor fan 13. The high-temperature and high-pressure gas refrigerant condenses into a high-pressure liquid refrigerant (single-phase).

The high-pressure liquid refrigerant sent out from the outdoor heat exchanger 11 becomes a two-phase refrigerant of a low-pressure gas refrigerant and a liquid refrigerant by the expansion valve 9. The two-phase refrigerant flows into the indoor heat exchanger 5. In the indoor heat exchanger 5, heat exchange is performed between the flowing two-phase refrigerant and the air supplied by the indoor fan 7. In the two-phase state refrigerant, the liquid refrigerant evaporates to become a low-pressure gas refrigerant (single-phase). This heat exchange cools the room. The low-pressure gas refrigerant sent out from the indoor heat exchanger 5 flows into the compressor 3 via the four-way valve 15. The low-pressure gas refrigerant that has flowed into the compressor 3 is compressed to become a high-temperature and high-pressure gas refrigerant, and is discharged from the compressor 3 again. Hereinafter, this cycle is repeated.

Next, the heat exchanger applied as the outdoor heat exchanger 11 in the refrigeration cycle apparatus 1 described above will be specifically described.

Embodiment 1.
As shown in FIGS. 2 and 3, in the heat exchanger 21, a plurality of fins 23 are arranged at a distance from each other. Each fin 23 has a first end portion 24a and a second end portion 24b facing each other with a distance in the width direction (first direction), and is in a direction intersecting the width direction (second direction). It extends in a strip shape.

As shown in FIG. 3, an adsorbent 31 is applied (formed) to the surface of each of the plurality of fins 23. The adsorbent 31a as the first part of the first adsorbent is applied to the region ER1 as the first part of the fin 23 extending from the first end portion 24a to the heat transfer tube 27. The adsorbent 31b as the second part of the first adsorbent is applied to the region ER2 as the second part of the fin 23 extending from the heat transfer tube 27 to the second end 24b. As shown in FIGS. 4 and 5, the adsorbent 31b is applied with a thickness thinner than the thickness of the adsorbent 31a. As the adsorbent 31, for example, silica gel and an epoxy resin are used. The heat exchanger 21 in which the adsorbent 31 is applied to the fins 23 is also called an absorption / desorption heat exchanger.

Next, the flow of air flowing between the fins 23 and the fins 23 when the heat exchanger 21 is operating will be described. It is assumed that air is flowing from the first end portion 24a side to the second end portion 24b side of the fin 23 by the outdoor fan 13 (see FIG. 1). In this case, the first end 24a of the fin 23 is located on the leeward side, and the second end 24b is located on the leeward side.

The air sent to the heat exchanger 21 flows from the side of the first end portion 24a toward the heat transfer tube 27 (air flow FL1, FL4). Next, it flows around the heat transfer tube 27 (air flow FL2, FL5). After that, it flows toward the side of the second end portion 24b (air flow FL3, FL6). At the portion of the fin 23 (region ER2) located on the leeward side of the heat transfer tube 27, the air flow is obstructed by the heat transfer tube 27.

Therefore, the wind speeds of the air flows FL3 and FL6 are smaller than the wind speeds of the air flows FL1, FL4, FL2, and FL5 flowing through the portion of the fin 23 (region ER1) located on the windward side of the heat transfer tube 27. .. As a result, the amount of moisture (water vapor amount) sent by air to the portion of the fin 23 located on the leeward side is smaller than the amount of moisture sent to the portion of the fin 23 located on the leeward side.

Here, as a comparative example, a heat exchanger in which the adsorbent is applied to the fins with a uniform thickness will be described. For convenience of explanation, the same members as those of the heat exchanger according to the embodiment are designated by the same reference numerals, and the description will not be repeated unless necessary.

As shown in FIGS. 6, 7 and 8, in the fin 23 of the heat exchanger according to the comparative example, the adsorbent 31 has a uniform thickness from the first end portion 24a to the second end portion 24b of the fin 23. It is formed with heat.

Next, the flow of air flowing between the fins 23 and the fins 23 will be described. The direction of air flow is the same as the direction shown in FIG. As shown in FIG. 6, the air sent to the heat exchanger 21 flows from the side of the first end portion 24a toward the heat transfer tube 27 (air flow FL7, FL10). Next, it flows around the heat transfer tube 27 (air flow FL8, FL11). After that, it flows toward the side of the second end portion 24b (air flow FL9, FL12).

At the portion of the fin 23 (region ER2) located on the leeward side of the heat transfer tube 27, the air flow is obstructed by the heat transfer tube 27. Therefore, the wind speeds of the air flows FL9 and FL12 on the leeward side are smaller than the wind speeds of the air flows FL7, FL10, FL8, and FL11 on the leeward side, and the fins 23 located on the leeward side (region ER2) are located. The amount of water (moisture content, water vapor amount) sent is smaller than the amount of water (moisture content, water vapor amount) sent to the fin 23 portion (region ER1) located on the windward side.

However, the adsorbent 31 is formed with a uniform thickness from the first end portion 24a to the second end portion 24b of the fin 23. Therefore, the amount of water that can be adsorbed (the amount of moisture and the amount of water vapor) in the portion of the fin 23 located on the leeward side (region ER2) is the amount of water that can be adsorbed in the portion of the fin 23 located on the leeward side (region ER1). While it is the same as (moisture content, water vapor amount), the amount of water (moisture content, water vapor amount) that can be actually adsorbed is small, and the adsorbent 31 is located on the leeward side of the fin 23 (region ER2). Is overcoated.

In contrast to the heat exchanger according to the comparative example, in the heat exchanger according to the first embodiment, 21 is an adsorbent formed in a portion (region ER2) of fins 23 located on the leeward side of the heat transfer tube 27. The 31b is formed with a thickness thinner than the thickness of the adsorbent 31a formed in the portion of the fin 23 (region ER1) located on the windward side of the heat transfer tube 27.

As a result, the adsorbent 31b corresponding to the small amount of water (moisture content, water vapor amount) is applied to the fin 23 portion (region ER2) located on the leeward side where the amount of moisture sent is smaller than that on the windward side. Will be there. As a result, the cost due to excessive application of the adsorbent 31 can be suppressed, which can contribute to the reduction of the production cost of the heat exchanger 21.

Embodiment 2.
The heat exchanger according to the second embodiment will be described. As shown in FIGS. 9, 10 and 11, the portion of the adsorbent 31c formed in the portion of the fin 23 (region ER2) located on the leeward side of the heat transfer tube 27 is relative to the heat transfer tube 27. It is formed with a thickness thinner than the thickness of the portion of the adsorbent 31c formed in the portion of the fin 23 (region ER1) located on the windward side.

In this heat exchanger 21 (see FIG. 2), the thickness of the adsorbent 31c (31) gradually decreases from the first end portion 24a of the fin 23 to the second end portion 24b via the heat transfer tube 27. It is formed like this. Since the other configurations are the same as those of the heat exchangers shown in FIGS. 2 and 3, the same members are designated by the same reference numerals, and the description thereof will not be repeated unless necessary.

Next, the flow of air flowing between the fins 23 and the fins 23 will be described. As shown in FIG. 9, the air sent to the heat exchanger 21 flows from the side of the first end portion 24a toward the heat transfer tube 27 (air flow FL13, FL16). Next, the air flows around the heat transfer tube 27 (air flow FL14, FL17). After that, the air flows toward the side of the second end portion 24b (air flow FL15, FL18).

As described above, in the portion of the fin 23 (region ER2) located on the leeward side of the heat transfer tube 27, the air flow is obstructed by the heat transfer tube 27. Therefore, the wind speeds of the air flows FL15 and FL18 on the leeward side of the heat transfer tube 27 are smaller than the wind speeds of the air flows FL13, FL16, FL14, and FL17 on the leeward side of the heat transfer tube 27.

In the heat exchanger 21 described above, the adsorbent 31c (31) is formed so as to gradually decrease in thickness from the first end portion 24a of the fin 23 to the second end portion 24b via the heat transfer tube 27. ing. The thickness of the portion of the adsorbent 31c formed in the portion of the fin 23 located on the leeward side of the heat transfer tube 27 (region ER2) is the portion of the fin 23 located on the windward side of the heat transfer tube 27 (region ER2). It is thinner than the thickness of the portion of the adsorbent 31c formed in the region ER1).

As a result, as described in the first embodiment, the portion of the fin 23 (region ER2) located on the leeward side where the amount of water (moisture content, water vapor amount) sent is smaller than that on the windward side has a small amount of water. The adsorbent 31b corresponding to (moist content, water vapor amount) is applied. As a result, the cost due to excessive application of the adsorbent 31 can be suppressed, which can contribute to the reduction of the production cost of the heat exchanger 21.

By the way, when moisture (moisture, water vapor) in the air is adsorbed on the adsorbent, the adsorbent generates heat. A thicker adsorbent 31c is applied to the fin 23 on the leeward side, where more water (moisture, water vapor) is sent than on the leeward side, in order to adsorb the water (moisture, water vapor). There is. Therefore, the calorific value of the adsorbent 31c is larger on the leeward side than on the leeward side.

As shown in FIGS. 12 and 13, in the heat exchanger 21 described above, the fin 23 is provided with a recess 25. The recess 25 is formed in a portion of the fin 23 located on the windward side of the heat transfer tube 27. In the heat exchanger 21, the adsorbent 31c is applied so as to cover the recess 25.

Therefore, the contact area between the adsorbent 31c and the fins 23 increases as compared with the case where there is no dent. As a result, the heat generated by the adsorbent 31c can be efficiently conducted to the fins 23 to remove the heat. As a result, the adsorption of water (moisture, water vapor) by the adsorbent 31c located on the windward side is promoted, and the dehumidifying performance can be improved.

Further, the adsorbent 31c is applied with a thickness that does not reflect the surface shape of the fin 23 in which the recess 25 is formed so that the surface of the adsorbent 31c does not have irregularities. As a result, it is possible to suppress the heat generated in the adsorbent 31c from being conducted into the air, and it is possible to prevent an excessive rise in the temperature of the air after dehumidification. As a result, comfort can be improved.

The fin 23 is not limited to the recess 25 as long as the contact area between the fin 23 and the adsorbent 31 can be increased, and for example, a corrugated fin may be applied.

Embodiment 3.
The heat exchanger according to the third embodiment will be described. As shown in FIG. 14, the heat exchanger 21 includes a first heat exchanger 21a, a second heat exchanger 21b, and a third heat exchanger 21c. The first heat exchanger 21a is composed of a plurality of first fins 23a and a heat transfer tube 27 as a first heat transfer tube. The second heat exchanger 21b is composed of a plurality of second fins 23b and a heat transfer tube 27 as a second heat transfer tube. The third heat exchanger 21c is composed of a plurality of third fins 23c and a heat transfer tube 27.

In each of the first heat exchanger 21a, the second heat exchanger 21b, and the third heat exchanger 21c, a plurality of fins 23 are arranged at intervals from each other, and heat transfer tubes are provided so as to penetrate the plurality of fins 23. 27 is inserted. The heat transfer tubes 27 are arranged so as to be spaced apart from each other in the direction in which the fins 23 extend. Here, from the windward side, the first heat exchanger 21a is arranged in the first row, the second heat exchanger 21b is arranged in the second row, and the third heat exchanger 21c is arranged in the third row. ..

As shown in FIG. 15, the adsorbent 31 is applied to the surface of each of the plurality of first fins 23a in the first row. The adsorbent 31a is applied to the first portion (region ER1) of the first fin 23a extending from the first end portion 24a to the heat transfer tube 27. The adsorbent 31b is applied to the second portion (region ER2) of the first fin 23a from the heat transfer tube 27 to the second end portion 24b. As shown in FIGS. 16 and 17, the adsorbent 31b is applied with a thickness thinner than the thickness of the adsorbent 31a.

An adsorbent 31 is applied to the surface of each of the plurality of second fins 23b in the second row. The adsorbent 31d as the first part of the second adsorbent is applied to the first portion (region ER3) of the second fin 23b extending from the third end portion 24c to the heat transfer tube 27. The adsorbent 31f as the second part of the second adsorbent is applied to the second portion (region ER4) of the second fin 23b extending from the heat transfer tube 27 to the fourth end portion 24d. The remaining portion of the second fin 23b is coated with the adsorbent 31e. As shown in FIGS. 16 and 17, the adsorbents 31d and 31f are applied with a thickness thinner than the thickness of the adsorbent 31a applied to the first fin 23a.

An adsorbent 31 is applied to the surface of each of the plurality of third fins 23c in the third row. 31 g of an adsorbent is applied to the first portion (region ER5) of the third fin 23c extending from the fifth end portion 24e to the heat transfer tube 27. The adsorbent 31i is applied to the second portion (region ER6) of the third fin 23c extending from the heat transfer tube 27 to the sixth end portion 24f. The remaining portion of the third fin 23c is coated with the adsorbent 31h. As shown in FIGS. 16 and 17, the adsorbents 31g and 31i are applied with a thickness thinner than the thickness of the adsorbent 31a applied to the first fin 23a.

Next, the flow of air flowing between the fins 23 and the fins 23 will be described. As shown in FIGS. 14 and 15, the air sent to the heat exchanger 21 first flows through the first heat exchanger 21a. In the first heat exchanger 21a, air flows from the side of the first end portion 24a of the first fin 23a toward the heat transfer tube 27 (air flow FL19, FL22). Next, the air flows around the heat transfer tube 27 (air flow FL20, FL23). After that, the air flows toward the side of the second end portion 24b (air flow FL21, FL24).

The air that has flowed through the first heat exchanger 21a then flows through the second heat exchanger 21b. In the second heat exchanger 21b, air flows from the side of the third end 24c of the second fin 23b toward the heat transfer tube 27 (air flow FL25, FL28). Next, the air flows around the heat transfer tube 27 (air flow FL26, FL29). After that, the air flows toward the side of the fourth end portion 24d (air flow FL27, FL30).

The air that has flowed through the second heat exchanger 21b then flows through the third heat exchanger 21c. In the third heat exchanger 21c, air flows from the side of the fifth end portion 24e of the third fin 23c toward the heat transfer tube 27 (air flow FL31, FL34). Next, the air flows around the heat transfer tube 27 (air flow FL32, FL35). After that, the air flows toward the side of the sixth end portion 24f (air flow FL34, FL36). In the heat exchanger 21, the heat transfer tubes 27 of the first heat exchanger 21a, the second heat exchanger 21b, and the third heat exchanger 21c are arranged along the direction in which air flows.

In the first heat exchanger 21a, the air flow is obstructed by the heat transfer tube 27 in the portion of the first fin 23a (region ER2) located on the leeward side of the heat transfer tube 27. Therefore, the wind speeds of the air flows FL21 and FL24 on the leeward side of the heat transfer tube 27 are smaller than the wind speeds of the air flows FL19, FL22, FL20, and FL23 on the leeward side of the heat transfer tube 27.

The second heat exchanger 21b and the third heat exchanger 21c are affected by the heat transfer tube 27 (air passage resistance) of the first heat exchanger 21a located on the windward side. Therefore, in the second heat exchanger 21b, the wind speeds of the air flows FL25 and FL28 on the windward side of the second fins 23b and the wind speeds of the air flows FL27 and FL30 on the leeward side are the same as those of the first heat exchanger 21a. The windward air flow is smaller than the wind speeds of FL19, FL22, FL20, and FL23.

Further, in the third heat exchanger 21c, the wind speeds of the air flows FL31 and FL34 on the windward side of the third fin 23c and the wind speeds of the air flows FL34 and FL36 on the leeward side are the wind speeds of the first heat exchanger 21a. The upper air flow is smaller than the wind speeds of FL19, FL22, FL20, and FL23.

In the heat exchanger 21 described above, the thickness of the adsorbent 31d applied to the portion (region ER3) of the second fin 23b located on the windward side of the heat transfer tube 27 of the second heat exchanger 21b and the leeward side. The thickness of the adsorbent 31f applied to the portion of the second fin 23b (region ER4) located in is thinner than the thickness of the adsorbent 31a applied to the first fin 23a.

Further, the thickness of the adsorbent 31 g applied to the portion (region ER5) of the third fin 23c located on the windward side with respect to the heat transfer tube 27 of the third heat exchanger 21c, and the thickness of the third fin located on the leeward side. The thickness of the adsorbent 31i applied to the portion 23c (region ER6) is thinner than the thickness of the adsorbent 31a applied to the first fin 23a.

As a result, as described in the first embodiment, the second heat exchange is located on the leeward side where the amount of water (moisture content, water vapor amount) sent is smaller than that on the windward side of the first heat exchanger 21a. The portion of the second fin 23b (regions ER3, ER4) of the vessel 21b and the portion of the third fin 23c (regions ER5, ER6) of the third heat exchanger 21c correspond to the small amount of water (moisture content, water vapor amount). The adsorbents 31d, 31f, 31g and 31i are applied. As a result, even in the heat exchanger 21 composed of a plurality of rows, the cost due to excessive application of the adsorbent 31 can be suppressed, which can contribute to the reduction of the production cost of the heat exchanger 21.

Embodiment 4.
In the fourth embodiment, an example of a step of applying the adsorbent to the fin through which the heat transfer tube is inserted will be described in a series of manufacturing steps of the heat exchanger.

As shown in FIG. 18, the chemical solution 45 containing the adsorbent is stored in the container 43 of the coating device 41. The adsorbent also contains an adhesive, and for example, silica gel and an epoxy resin are used. Above the container 43, a heat exchanger 21 in the process of being assembled, in which the heat transfer tube 27 is inserted into the fin 23, is arranged. The heat exchanger 21 is lowered toward the container 43 (chemical solution 45), and as shown in FIG. 19, the heat exchanger 21 is immersed in the chemical solution 45 with the longitudinal direction of the fins 23 horizontal.

After immersing the heat exchanger 21 in the chemical solution 45 for a certain period of time, the heat exchanger 21 is pulled up from the chemical solution 45 as shown in FIG. The heat exchanger 21 is pulled up above the container 43 to hold the fins 23 in a horizontal longitudinal direction. During that time, the excess chemical solution adhering to the fins 23 and the like of the heat exchanger 21 drips due to gravity (arrow GR, see FIG. 21), and the chemical solution left on the fins 23 is dried and applied as an adsorbent. become. As shown in FIGS. 21, 22 and 23, the amount of the adsorbent applied to the lower first end portion 24a of the fin 23 is increased by the surface tension of the chemical solution 45 as compared with the upper second end portion 24b. .. In this way, the application of the adsorbent 31 to the heat exchanger 21 is completed.

The heat exchanger 21 manufactured by the manufacturing method described above is arranged so that the lower first end portion 24a of the fin 23, to which the adsorbent 31 is more coated, is located on the windward side. As a result, similarly to the heat exchanger 21 described in the first embodiment, the amount of water delivered (moisture content, water vapor amount) is smaller in the fin 23 located on the leeward side than in the wind side. The adsorbent 31b corresponding to the amount (moisture content, water vapor amount) is applied. As a result, the cost due to the excessive application of the adsorbent 31 can be suppressed, which can contribute to the reduction of the production cost.

As a pattern of applying the adsorbent 31 to the fins 23, the adsorbent 31b formed in the portion of the fins 23 located on the leeward side of the heat transfer tube 27 is the fins located on the windward side of the heat transfer tube 27. It suffices that it is formed with a thickness thinner than the thickness of the adsorbent 31a formed in the portion 23.

For example, as shown in FIGS. 24 and 25, the adsorbent 31a is applied to the windward side and the adsorbent 31b is applied to the leeward side in a manner in which the width direction of the fins 23 is divided into two with the vicinity of the center of the heat transfer tube 27 as a boundary. The coated heat exchanger 21 may be used. Further, as shown in FIGS. 26 and 27, the adsorbent 31b is applied to the region of the fin 23 behind the heat transfer tube 27 when viewed from the windward side, and the adsorbent 31a is applied to the other region of the fin 23. The heat exchanger 21 may be used.

Although the heat exchanger 21 according to each of the above-described embodiments has been described when it is applied to the outdoor heat exchanger, it may be applied to the indoor heat exchanger.

The heat exchangers described in each embodiment can be combined in various ways as needed.

The embodiments disclosed this time are examples and are not limited thereto. The present invention is shown by the claims, not the scope described above, and is intended to include all modifications in the sense and scope equivalent to the claims.

The present invention is effectively used in a heat exchanger provided with fins coated with an adsorbent.

1 Refrigeration cycle device, 3 Compressor, 5 Indoor heat exchanger, 7 Indoor fan, 9 Expansion valve, 11 Outdoor heat exchanger, 13 Outdoor fan, 15 Four-way valve, 17 Refrigerant piping, 21 Heat exchanger, 21a First heat Exchanger, 21b 2nd heat exchanger, 21c 3rd heat exchanger, 23, fins, 23a 1st fin, 23b 2nd fin, 23c 3rd fin, 24a 1st end, 24b 2nd end, 24c second 3 end, 24d 4th end, 24e 5th end, 24f 6th end, 24g 1st end, 24h 2nd end, 25 depressions, 27 heat transfer tubes, 31, 31a, 31b, 31c, 31d , 31e, 31f, 31g, 31h, 31i Adsorbent, 41 Coating device, 43 Container, 45 Chemical solution, ER1, ER2, ER3, ER4, ER5, ER6 region, FL, FL1-FL36 Air flow, GR arrow.

Claims (5)

A first fin having a first end and a second end facing each other with a distance in the first direction and extending in a second direction intersecting the first direction, the first end, and the first. It is provided with a first heat transfer tube inserted into the portion of the first fin located between the two ends and a first adsorbent formed on the first fin.
The first adsorbent is
The first part of the first adsorbent formed in the first part of the first fin from the first end portion to the first heat transfer tube, and
Includes a second part of the first adsorbent formed in the second part of the first fin from the first heat transfer tube to the second end.
The thickness of the second part of the first adsorbent is thinner than the thickness of the first part of the first adsorbent.
In the first fin, the first end is located on the leeward side and the second end is located on the leeward side.
The second portion of the first fin is a heat exchanger located in a region on the leeward side of the first heat transfer tube. The heat exchanger according to claim 1, wherein a recess is formed in the first portion of the first fin. It has a third end and a fourth end that are arranged on the side of the second end with respect to the first fin and face each other with a distance in the first direction, and extend in the second direction. 2nd fin and
It contains a second heat transfer tube inserted into the portion of the second fin located between the third end portion and the fourth end portion and a second adsorbent formed on the second fin.
The second adsorbent is
The first part of the second adsorbent formed in the third part of the second fin from the third end to the second heat transfer tube,
Includes a second part of the second adsorbent formed in the fourth part of the second fin from the second heat transfer tube to the fourth end.
The heat exchanger according to claim 1, wherein the thickness of each of the first part of the second adsorbent and the second part of the second adsorbent is thinner than the thickness of the first part of the first adsorbent. The heat exchanger according to claim 1, wherein the first adsorbent contains silica gel and an epoxy resin. A refrigeration cycle apparatus comprising the heat exchanger according to any one of claims 1 to 4.

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