WO2022244461A1 - Heat exchange system - Google Patents

Abstract

This heat exchange system for performing heat exchange between a refrigerant and air comprises: a cooler (22) for cooling air by means of a refrigerant; and a radiator (20) that causes heat to be dissipated from the refrigerant to air. The radiator is positioned below the cooler and arranged so that condensed water (Wc) generated by the cooler flows downward toward the radiator. The radiator has a specific configuration (207). The specific configuration causes the moisture of condensed water flowing down to the radiator to be spread out more at the radiator than cases in which the radiator is not equipped with the specific configuration.

Description

heat exchange system Cross-references to related applications

This application is based on Japanese Patent Application No. 2021-84033 filed on May 18, 2021, the contents of which are incorporated herein by reference.

The present disclosure relates to a heat exchange system that exchanges heat between refrigerant and air.

For example, a vehicle air conditioner disclosed in Patent Document 1 includes an evaporator and a condenser, and the evaporator and condenser constitute the heat exchange system. The evaporator and condenser are housed in one housing. Also, the condenser is arranged below the evaporator, and is provided with a conduit for guiding the condensed water generated in the evaporator to the condenser.
In the air conditioner disclosed in Patent Document 1, condensed water from the evaporator is applied to the condenser to raise the cooling efficiency of the refrigerant in the condenser, thereby improving the efficiency of the entire refrigeration cycle including the evaporator and the condenser.

WO2018/235765

Certainly, in order to improve the cooling efficiency of cooling the refrigerant in a radiator such as a condenser, it is effective to pour water (for example, condensed water) over the radiator. In this case, it is necessary to smoothly guide condensed water generated in a cooler such as an evaporator to a radiator. This is because, if the flow of water from the cooler to the radiator is interrupted, a situation may occur in which the water remaining in the cooler scatters, or the heat exchange in the radiator is insufficient.

However, Patent Document 1 makes no mention of smoothly guiding the condensed water generated in the cooler to the radiator. As a result of detailed studies by the inventors, the above was found.

In view of the above points, the present disclosure aims to provide a heat exchange system that can smoothly guide condensed water generated in a cooler to a radiator.

To achieve the above objects, according to one aspect of the present disclosure, a heat exchange system includes:
A heat exchange system for exchanging heat between a refrigerant and air,
a cooler that cools air with a refrigerant;
A radiator located below the cooler, arranged so that condensed water generated in the cooler flows down, has a specific configuration, and dissipates heat from the refrigerant to the air,
The specific configuration is a radiator, which allows condensed water that has flowed down to the radiator to wet and spread more than when the specific configuration is not provided.

By doing so, the condensed water generated in the cooler is more likely to be pulled toward the radiator due to the specific configuration of the radiator. Therefore, the condensed water is less likely to stay in the cooler, and the condensed water can be smoothly guided to the radiator.

It should be noted that the reference numerals in parentheses attached to each component etc. indicate an example of the correspondence relationship between the component etc. and the specific component etc. described in the embodiment described later.

1 is a refrigerant circuit diagram showing a refrigeration cycle circuit having a heat exchanger of a first embodiment; FIG. It is a sectional view showing typically a schematic structure of a heat exchanger in a 1st embodiment. FIG. 3 is a diagram showing, in section III-III of FIG. 2, an excerpt of a laminated structure constituting the heat exchanger of the first embodiment; FIG. 3 is a view showing an excerpt from the laminated structure constituting the heat exchanger of the first embodiment in the IV-IV cross section of FIG. 2; FIG. 4 is a cross-sectional view schematically showing a partial cross-section of the condensation tube portion obtained by cutting the plate material constituting the condensation tube portion so as to reveal the thickness of the plate material constituting the condensation tube portion in the first embodiment, and showing the configuration of the condensation portion. FIG. 2 is a diagram in which, in addition to the reference numerals, reference numerals indicating the configuration of the evaporating section are also written. FIG. 4 is a cross-sectional view schematically showing a partial cross-section of a condensation fin obtained by cutting the plate material constituting the condensation fin so that the thickness of the plate material constituting the condensation fin is exposed in the first embodiment; In addition to , reference numerals indicating the configuration of the evaporator are also shown. FIG. 5 is a cross-sectional view schematically showing the VII-VII cross section of FIG. 1 is a cutaway view of FIG. FIG. 10 is a schematic perspective view of a single condensation fin extracted and partially enlarged in the second embodiment. FIG. 9 is a cross-sectional view schematically showing the IX-IX cross section of FIG. 8 in the second embodiment, and is a portion of the condensation fin obtained by cutting along a plane perpendicular to the direction in which the fine grooves provided in the condensation fin extend. 1 is a diagram showing a typical cross section; FIG. FIG. 10 is a perspective view schematically showing the condensation fins and the condensation tube portions adjacent to the condensation fins in the second embodiment, in which the flow of condensed water flowing from the condensation tube portions to the condensation fins is indicated by dashed arrows; is. FIG. 5 is a view corresponding to FIG. 4 , showing an excerpt of a laminated structure constituting a heat exchanger in the third embodiment; FIG. 12 is a sectional view showing the XII-XII section of FIG. 11 in the third embodiment; FIG. 12 is a perspective view schematically showing an enlarged portion XIII of FIG. 11 in the third embodiment; FIG. 5 is a view corresponding to FIG. 4 , showing an excerpt of a laminated structure constituting a heat exchanger in the fourth embodiment; FIG. 15 is a schematic enlarged view of the portion corresponding to the XV portion of FIG. 14 in the fifth embodiment, showing a plurality of grooves formed in the intermediate surface. FIG. 10 is a view corresponding to FIG. 4 , showing an excerpt of the laminated structure constituting the heat exchanger in the sixth embodiment. FIG. 17 is a diagram schematically showing an enlarged portion corresponding to the XVII portion of FIG. 16 in the seventh embodiment, showing a plurality of condensation section surface grooves formed on the surface of the condensation section. FIG. 11 is a cross-sectional view schematically showing the schematic configuration of a heat exchanger in an eighth embodiment, corresponding to FIG. 2 ; FIG. 19 is a view corresponding to FIG. 4, showing the condenser section and the evaporator section of the heat exchanger of the eighth embodiment, taken along the XIX-XIX section of FIG. 18; FIG. 11 is a view corresponding to FIG. 4 , showing a condensing section, an evaporating section, and an intermediate section that constitute a heat exchanger in a ninth embodiment; FIG. 10 is a perspective view showing a unit in which a heat exchanger with a condenser and an evaporator, a pressure reducing device, and an accumulator are integrated in another embodiment. FIG. 5 is a view corresponding to FIG. 4 and showing an extract of a laminated structure constituting a heat exchanger in another embodiment. FIG. 21 is a view corresponding to FIG. 20 and showing an extract of a laminated structure constituting a heat exchanger in another embodiment.

Each embodiment will be described below with reference to the drawings. In addition, in each of the following embodiments, the same or equivalent portions are denoted by the same reference numerals in the drawings.

(First embodiment)
As shown in FIGS. 1 and 2, in this embodiment, a heat exchanger 10 is provided as a heat exchange system for exchanging heat between refrigerant and air. For example, the heat exchanger 10 is used in a vehicle air conditioner and constitutes part of a refrigeration cycle circuit 12 that is included in the vehicle air conditioner and in which a refrigerant circulates. A vehicle air conditioner air-conditions a vehicle interior, which is a space to be air-conditioned.

In the refrigerating cycle circuit 12, the refrigerant compressed by the compressor 14 included in the refrigerating cycle circuit 12 flows into the condenser section 20 that constitutes a part of the heat exchanger 10 and functions as a radiator. heat is exchanged with The refrigerant that has exchanged heat with the air in the condenser section 20 is decompressed and expanded by the decompression device 15, flows from the decompression device 15 into the evaporator section 22 that constitutes a part of the heat exchanger 10 and functions as a cooler, and then flows into the evaporator section. At 22, it is made to exchange heat with air. The refrigerant that has exchanged heat with the air in the evaporator 22 flows into the accumulator 16, which is a gas-liquid separator, where it is separated into gas and liquid. Of the refrigerant separated into gas and liquid by the accumulator 16 , the gas-phase refrigerant flows out of the accumulator 16 and is sucked into the compressor 14 . On the other hand, of the refrigerant separated into gas and liquid by the accumulator 16 , the liquid-phase refrigerant is stored in the accumulator 16 . Incidentally, the decompression device 15 is, for example, a capillary tube, an orifice, or an expansion valve.

For example, the evaporator 22 of the heat exchanger 10 is arranged in the first air passage through which air flows toward the air-conditioned space, and cools the air flowing through the first air passage with a refrigerant. Also, the condenser section 20 of the heat exchanger 10 is arranged in the second air passage through which the air discharged to the outside of the air-conditioned space flows, and releases heat from the refrigerant to the air flowing through the second air passage.

As shown in FIG. 2, the heat exchanger 10 of the present embodiment is constructed by brazing together a plurality of constituent members made of metal such as aluminum alloy or copper alloy. In addition to the condenser section 20 and the evaporator section 22, the heat exchanger 10 includes an intermediate section 24, one side plate section 30, the other side plate section 32, a condenser inlet pipe 34, a condenser outlet pipe 35, and an evaporator. A section inlet pipe 36 and an evaporator section outlet pipe 37 are provided.

The one-side side plate portion 30 and the other-side side plate portion 32 are formed in a plate shape with a predetermined stacking direction Ds as the thickness direction. As shown in FIGS. 2 to 4, the evaporating section 22 and the condensing section 20 are arranged in the order of the evaporating section 22 and the condensing section 20 from one side in the heat exchanger vertical direction Dv that matches the alignment direction. An intermediate section 24 is arranged between the evaporating section 22 and the condensing section 20 .

As shown in FIGS. 3 and 4, the heat exchanger 10 is arranged in a posture inclined with respect to the vertical direction Dg (in other words, the vertical direction Dg) when mounted on a vehicle. The vertical direction Dv is oblique to the vertical direction Dg. One side in the longitudinal direction Dv of the heat exchanger is positioned above the other side. Therefore, the evaporating section 22, the intermediate section 24, and the condensing section 20 are arranged side by side in the order of the evaporating section 22, the intermediate section 24, and the condensing section 20 from the upper side in the vertical direction Dg. For example, the condensation section 20 is arranged to overlap the evaporation section 22 downward in the vertical direction Dg, and the intermediate section 24 is provided between the condensation section 20 and the evaporation section 22 . Therefore, when condensed water Wc is generated in the evaporating section 22 as the air is cooled, the condensed water Wc flows down from the evaporating section 22 to the condensing section 20 through the intermediate section 24 .

As shown in FIGS. 2 to 4, the stacking direction Ds is a direction intersecting the vertical direction Dg and the heat exchanger vertical direction Dv, or strictly speaking, a direction perpendicular to each. Moreover, in this embodiment, the direction perpendicular to both the stacking direction Ds and the heat exchanger vertical direction Dv is referred to as the heat exchanger width direction Dw. Further, in the description of the present embodiment, unless otherwise specified, "upper side" means the upper side when mounted on the vehicle (i.e., the upper side of the vehicle), and "lower side" means the lower side when mounted on the vehicle (i.e., the upper side of the vehicle). , vehicle underside).

The one side plate portion 30 is arranged at one end of the heat exchanger 10 in the stacking direction Ds, and the other side plate portion 32 is arranged at the other end of the heat exchanger 10 in the stacking direction Ds. It is The condensation section 20, the evaporation section 22, and the intermediate section 24 are arranged between the one side plate section 30 and the other side plate section 32 in the stacking direction Ds. It is sandwiched between 32 and Condensing section 20 and evaporating section 22 are fixed to one side plate section 30 and other side plate section 32, respectively, and intermediate section 24 is fixed to condensing section 20 and evaporating section 22, respectively.

One side plate portion 30 is provided with a condenser inlet pipe 34 and an evaporator outlet pipe 37, and the other side plate portion 32 is provided with a condenser outlet pipe 35 and an evaporator inlet pipe 36. there is As shown in FIGS. 1 and 2 , the condenser inlet pipe 34 is connected to the refrigerant flow upstream side of the condenser 20 and causes the refrigerant discharged from the compressor 14 to flow into the condenser 20 . The condenser outlet pipe 35 is connected to the refrigerant flow downstream side of the condenser 20 and causes the refrigerant in the condenser 20 to flow out from the condenser 20 to the decompression device 15 . The evaporator inlet pipe 36 is connected to the refrigerant flow upstream side of the evaporator 22 and allows the refrigerant from the decompression device 15 to flow into the evaporator 22 . The evaporator outlet pipe 37 is connected to the refrigerant flow downstream side of the evaporator 22 and causes the refrigerant in the evaporator 22 to flow out from the evaporator 22 to the accumulator 16 .

As shown in FIGS. 2 to 4, the condensation section 20 has a first condensation tank section 201, a second condensation tank section 203, a plurality of condensation tube sections 205, and a plurality of condensation fins 206. The condensation section 20 exchanges heat between the refrigerant flowing in the condensation tube section 205 and the air passing through the condensation section 20, and the heat exchange causes the refrigerant to release heat to the air, thereby condensing the refrigerant.

The first condensation tank portion 201 is provided on one side of the plurality of condensation tube portions 205 in the heat exchanger vertical direction Dv, and the second condensation tank portion 203 is provided on one side of the plurality of condensation tube portions 205 in the heat exchanger vertical direction Dv. provided on the other side. The first condensation tank portion 201 has a plurality of first condensation tank constituent portions 202 arranged in series in the stacking direction Ds, and is configured by joining the plurality of first condensation tank constituent portions 202 to each other. . Therefore, the first condensation tank portion 201 is formed to extend in the stacking direction Ds.

Between the first condensing tank forming portions 202 adjacent to each other, basically, the internal spaces 202a of the first condensing tank forming portions 202 communicate with each other through through holes. However, in the C1 portion (see FIG. 2), the communication between the internal spaces 202a of the first condensing tank forming portions 202 adjacent to each other is blocked.

The second condensation tank portion 203 has a plurality of second condensation tank constituent portions 204 arranged in series in the stacking direction Ds, and is configured by joining the plurality of second condensation tank constituent portions 204 to each other. . Therefore, the second condensation tank portion 203 is formed to extend in the stacking direction Ds.

Between the mutually adjacent second condensation tank constituent parts 204, basically, the internal spaces 204a of the second condensation tank constituent parts 204 communicate with each other through through holes. However, communication between the inner spaces 204a of the second condensing tank forming portions 204 adjacent to each other is cut off at the C2 and C3 portions (see FIG. 2).

The condensation tube portion 205 corresponds to the radiator tube of the present disclosure. The condensation tube portion 205 has a flat shape whose thickness direction is the stacking direction Ds. Inside the condensation tube portion 205, a condensation tube flow path 205a through which a refrigerant flows is formed. The condensation tube flow path 205a extends in a meandering manner while reciprocating in the longitudinal direction Dv of the heat exchanger. One end of the condensation tube channel 205 a is connected to the internal space 202 a of the first condensation tank component 202 , and the other end of the condensation tube channel 205 a is connected to the internal space 204 a of the second condensation tank component 204 .

Also, the plurality of condensing tube portions 205 are stacked so as to be spaced apart from each other in the stacking direction Ds. Ventilation spaces 20a through which air passes are formed between the condensing tube portions 205 adjacent to each other. That is, a plurality of ventilation spaces 20a are formed side by side in the stacking direction Ds.

An arrow FLa (see FIGS. 3 and 4) represents the flow of air flowing into the ventilation space 20a of the condensation section 20. As shown in FIG. That is, the air passing through the ventilation space 20a of the condenser section 20 flows with one side in the heat exchanger width direction Dw as the air flow upstream side and the other side in the heat exchanger width direction Dw as the air flow downstream side.

The condenser fins 206 correspond to radiator fins of the present disclosure. A plurality of condensation fins 206 are respectively arranged in the ventilation space 20 a of the condensation section 20 and brazed to the outside of the condensation tube section 205 adjacent to the condensation fins 206 . Specifically, the condensation fins 206 are corrugated fins, and the condensation fins 206 are formed with a plurality of louvers 206a (see FIG. 8). With such a configuration, the condensation fins 206 promote heat exchange between the air passing through the ventilation space 20 a of the condensation section 20 and the refrigerant in the condensation section 20 . Condensation fins 206 are made of a metal with good thermal conductivity, such as an aluminum alloy or a copper alloy.

As shown in FIG. 2, in the condensation section 20, refrigerant from the compressor 14 (see FIG. 1) is provided at one end of the second condensation tank section 203 in the stacking direction Ds. It flows into the internal space 204 a of the section 204 via the condensation section inlet pipe 34 . In the first condensation tank portion 201 and the second condensation tank portion 203, the refrigerant flows from one side to the other side in the stacking direction Ds. At the same time, in each of the plurality of condensation tube portions 205, the refrigerant flows from the first condensation tank forming portion 202 side to the second condensation tank forming portion 204 side, or from the second condensation tank forming portion 204 side to the first condensation tank forming portion. It flows to the part 202 side. Arrow A1 in FIG. 2 indicates the refrigerant flow in the first condensing tank portion 201, arrow A2 indicates the refrigerant flow in the second condensing tank portion 203, and arrow A3 indicates the refrigerant flow in the condensing tube portion 205. showing.

The refrigerant that has flowed through the condensation section 20 in this way flows from the internal space 204 a of the second condensation tank forming section 204 provided at the end of the second condensation tank section 203 on the other side in the stacking direction Ds to the condensation section outlet pipe 35 . to the decompression device 15 (see FIG. 1).

As shown in FIGS. 2 to 4, the evaporating section 22 has a first evaporating tank section 221, a second evaporating tank section 223, a plurality of evaporating tube sections 225, and a plurality of evaporating fins 226. The evaporating portion 22 exchanges heat between the refrigerant flowing through the evaporating tube portion 225 and the air passing through the evaporating portion 22, and the heat exchange evaporates the refrigerant and cools the air.

The first evaporation tank portion 221 is provided on one side of the plurality of evaporation tube portions 225 in the heat exchanger vertical direction Dv, and the second evaporation tank portion 223 is provided on one side of the plurality of evaporation tube portions 225 in the heat exchanger vertical direction Dv. provided on the other side. The first evaporation tank portion 221 has a plurality of first evaporation tank constituent portions 222 arranged in series in the stacking direction Ds, and is configured by joining the plurality of first evaporation tank constituent portions 222 to each other. . Therefore, the first evaporation tank portion 221 is formed to extend in the stacking direction Ds.

Between the first evaporation tank constituent parts 222 adjacent to each other, basically, the internal spaces 222a of the first evaporation tank constituent parts 222 communicate with each other through through holes. However, in the E1 and E2 portions (see FIG. 2), communication between the internal spaces 222a of the first evaporation tank forming portions 222 adjacent to each other is blocked.

The second evaporation tank portion 223 has a plurality of second evaporation tank constituent portions 224 arranged in series in the stacking direction Ds, and is configured by joining the plurality of second evaporation tank constituent portions 224 to each other. . Therefore, the second evaporation tank portion 223 is formed to extend in the stacking direction Ds.

Between the mutually adjacent second evaporation tank constituent parts 224, the internal spaces 224a of the second evaporation tank constituent parts 224 basically communicate with each other through through holes. However, in the E3 portion (see FIG. 2), the communication between the internal spaces 224a of the second evaporation tank forming portions 224 adjacent to each other is blocked.

The evaporator tube section 225 corresponds to the cooler tube of the present disclosure. The evaporating tube portion 225 has a flat shape whose thickness direction is the stacking direction Ds. Inside the evaporating tube portion 225, an evaporating tube flow path 225a through which a refrigerant flows is formed. The evaporation tube flow path 225a extends in a meandering manner while reciprocating in the longitudinal direction Dv of the heat exchanger. One end of the evaporation tube flow path 225 a is connected to the internal space 222 a of the first evaporation tank forming part 222 , and the other end of the evaporation tube flow path 225 a is connected to the internal space 224 a of the second evaporation tank forming part 224 .

Also, the plurality of evaporating tube portions 225 are arranged in layers so as to be spaced apart from each other in the stacking direction Ds. Ventilation spaces 22a through which air passes are formed between the evaporating tube portions 225 adjacent to each other. That is, a plurality of ventilation spaces 22a are formed side by side in the stacking direction Ds.

An arrow FLb (see FIGS. 3 and 4) represents the flow of air flowing into the ventilation space 22a of the evaporator 22. That is, the air passing through the ventilation space 22a of the evaporating section 22 flows with one side in the heat exchanger width direction Dw as the air flow upstream side and the other side in the heat exchanger width direction Dw as the air flow downstream side.

The plurality of evaporating fins 226 are arranged in the ventilation space 22a of the evaporating part 22 and are brazed to the outside of the evaporating tube part 225 adjacent to the evaporating fins 226 . Specifically, the evaporation fins 226 are corrugated fins, and the evaporation fins 226 are formed with a plurality of louvers like the condensation fins 206 . With such a configuration, the evaporating fins 226 facilitate heat exchange between the air passing through the ventilation space 22 a of the evaporating section 22 and the refrigerant in the evaporating section 22 . Evaporation fins 226 are made of metal with good thermal conductivity, such as aluminum alloy or copper alloy.

As shown in FIG. 2, in the evaporating section 22, the refrigerant from the decompression device 15 (see FIG. 1) is provided at the end of the first evaporating tank section 221 on the other side in the stacking direction Ds. It flows into the internal space 222 a of the unit 222 through the evaporator inlet pipe 36 . In the first evaporation tank portion 221 and the second evaporation tank portion 223, the refrigerant flows from the other side to the one side in the stacking direction Ds. At the same time, in each of the plurality of evaporation tube portions 225, the refrigerant flows from the first evaporation tank forming portion 222 side to the second evaporation tank forming portion 224 side, or from the second evaporation tank forming portion 224 side to the first evaporation tank forming portion. It flows to the part 222 side. Arrow B1 in FIG. 2 indicates the refrigerant flow in the first evaporation tank portion 221, arrow B2 indicates the refrigerant flow in the second evaporation tank portion 223, and arrow B3 indicates the refrigerant flow in the evaporation tube portion 225. showing.

The refrigerant that has flowed through the evaporator 22 in this manner flows from the internal space 222 a of the first evaporator tank forming portion 222 provided at one end in the stacking direction Ds of the first evaporator tank 221 to the evaporator outlet pipe 37 . to the accumulator 16 (see FIG. 1).

Here, the configuration of the condensation section 20 and the evaporation section 22 of the heat exchanger 10 will be described in detail. As shown in FIGS. 2 to 4, the condensation section 20 and the evaporation section 22 are constructed by laminating a plurality of laminated structures 38 in the lamination direction Ds and brazing them together. The laminated structure 38, which is a tube sub-assembly, has a substantially flat shape whose thickness direction is the lamination direction Ds. The hand direction coincides with the heat exchanger width direction Dw.

Each of the plurality of laminated structures 38 is composed of a first plate member 381 and a second plate member 382 that are joined together by brazing to form a pair. Both the first plate member 381 and the second plate member 382 are made of a metal having good thermal conductivity, such as an aluminum alloy or a copper alloy.

Note that in FIG. 2, the cross sections of the first plate member 381, the second plate member 382, the condensation fins 206, and the evaporation fins 226 are indicated by thick lines instead of hatching. Also, in order to make the illustration easier to see, FIG. are displayed with a space between them). These are the same for later-described figures corresponding to FIG. 2 .

As shown in FIGS. 2 to 4, the first plate member 381 is arranged on one side in the stacking direction Ds with respect to the second plate member 382 in the laminate structure 38 including the first plate member 381. FIG. The first plate member 381 has a plate shape having a thickness in the stacking direction Ds, and is recessed toward one side in the stacking direction Ds so as to form a recessed space through which the coolant flows. On the other hand, the second plate member 382 has a plate shape having a thickness in the stacking direction Ds, and is recessed toward the other side in the stacking direction Ds so as to form a recessed space through which the coolant flows.

In each laminated structure 38, the first plate member 381 and the second plate member 382 are joined together in a posture in which the recessed space of the first plate member 381 and the recessed space of the second plate member 382 face each other. It is composed by

In addition, the internal spaces 202a and 204a of the first and second condensing tank components 202 and 204, the condensation tube flow path 205a, the internal spaces 222a and 224a of the first and second evaporation tank components 222 and 224, and the evaporation tube flow The path 225a is formed by combining the concave space of the first plate member 381 and the concave space of the second plate member 382 together.

That is, one laminated structure 38 includes one first condensation tank constituent portion 202, one second condensation tank constituent portion 204, one condensation tube constituent portion 205, one first evaporation tank constituent portion 222, and one second condensation tank constituent portion 222. It has two evaporation tank constituent parts 224 and one evaporation tube part 225 . In other words, the first condensation tank component 202, the second condensation tank component 204, the condensation tube component 205, the first evaporation tank component 222, the second evaporation tank component 224, and the evaporation tube component 225 are integrated. It's becoming

However, the condensation tube flow path 205a located on the most one side in the stacking direction Ds among the plurality of condensation tube flow paths 205a is formed by the second plate member 382 and the one side plate portion 30. As shown in FIG. Among the plurality of condensation tube flow paths 205 a , the condensation tube flow path 205 a located on the othermost side in the stacking direction Ds is formed by the first plate member 381 and the other side plate portion 32 . This is also true for the internal spaces 202a, 204a of the first and second condensing tank components 202, 204, the internal spaces 222a, 224a of the first and second evaporative tank components 222, 224, and the evaporative tube channel 225a. It is the same.

As shown in FIGS. 3 and 4, through-holes 38a are formed in the plurality of laminated structures 38, and the through-holes 38a separate the condensation section 20 and the evaporation section 22 in each of the laminated structures 38. It is arranged between the condensing section 20 and the evaporating section 22 as shown in FIG. This is to insulate between the condenser section 20 and the evaporator section 22 by the through holes 38a.

The intermediate portion 24 of the heat exchanger 10 is provided between the condensation portion 20 and the evaporation portion 22 as described above. is arranged in the middle of the path flowing from the evaporating section 22 to the condensing section 20 . For example, in the present embodiment, the intermediate portion 24 corresponds to the portion of the laminate structure 38 on one side and the portion on the other side of the through hole 38 a in the heat exchanger width direction Dw.

In addition, most of the condensed water Wc that flows down from the evaporating section 22 to the condensing section 20 passes through while wetting the outer surface of the intermediate section 24 . That is, the intermediate portion 24 is formed with an intermediate surface 241 disposed in the middle of the flow of the condensed water Wc from the evaporating portion 22 to the condensing portion 20, and the outer surface of the intermediate portion 24 corresponds to the intermediate surface 241. .

As shown in FIGS. 2, 5 and 6, the condensing section 20 has a specific configuration 207 for promoting the flow of the condensed water Wc from the evaporating section 22 to the condensing section 20. FIG. The specific configuration 207 of the condensation section 20 allows the condensed water Wc that has flowed down to the condensation section 20 to wet and spread in the condensation section 20 compared to the case where the specific configuration 207 is not provided.

Specifically, the specific configuration 207 of the condensation section 20 in this embodiment is the surface coating 207 a applied to the condensation section 20 . In other words, the condensation section 20 has a surface coating 207 a applied to the condensation section 20 as the specific configuration 207 . Accordingly, the surface coating 207 a is provided on the respective surfaces of the first condensing tank portion 201 , the second condensing tank portion 203 , the condensing tube portion 205 and the condensing fins 206 . 5 shows the surface coating 207a applied to the surface of the condensation tube portion 205, and FIG. 6 shows the surface coating 207a applied to the surface of the condensation fins 206. FIG.

The surface coating 207a of the condensation section 20 is a hydrophilic coating that improves the hydrophilicity of the surface of the condensation section 20 compared to when the surface coating 207a is not provided. The surface of the condensation section 20 is, for example, the surfaces of the first condensation tank section 201 , the second condensation tank section 203 , the condensation tube section 205 and the condensation fins 206 . For example, this surface coating 207a can be formed by surface treatment such as painting or plating. In the present embodiment, for example, the surface coating 207a is formed by immersing the heat exchanger 10 after brazing in a dip bath containing a liquid coating agent.

Therefore, in the heat exchanger 10 of the present embodiment, the same surface coating as the surface coating 207a of the condenser section 20 is applied to the entire heat exchanger 10 . That is, the evaporating section 22 is also coated with a surface coating 227 a , and the surface coating 227 a of the evaporating section 22 is the same hydrophilic coating as the surface coating 207 a of the condensing section 20 . Therefore, the surface coating 207 a of the condenser section 20 gives the surface of the condenser section 20 the same hydrophilicity compared to the evaporator section 22 .

In addition, since the surface coating 227a of the evaporating section 22 is also a hydrophilic coating, the surface coating 227a of the evaporating section 22 improves the hydrophilicity of the surface of the evaporating section 22 compared to the case where the surface coating 227a is not provided. The surface of the evaporating section 22 is, for example, the surfaces of the first evaporating tank section 221 , the second evaporating tank section 223 , the evaporating tube section 225 and the evaporating fins 226 . 5 and 6 each show a cross section of the condensation section 20. In FIGS. 5 and 6, reference numerals indicate the configuration of the evaporation section 22 corresponding to the configuration of the condensation section 20 shown in FIGS. are also listed.

Further, since the same surface coating as the surface coating 207a of the condenser section 20 is applied to the entire heat exchanger 10, the intermediate section 24 has the surface coating 24a applied to the intermediate surface 241 as shown in FIG. have. The surface coating 24a of the intermediate portion 24 is the same hydrophilic coating as the surface coatings 207a and 227a of the condensation portion 20 and the evaporation portion 22. FIG.

Therefore, the surface coating 24 a of the intermediate portion 24 gives the intermediate surface 241 the same hydrophilicity compared to the evaporator portion 22 . Also, since the surface coating 24a of the intermediate portion 24 is also a hydrophilic coating, the surface coating 24a of the intermediate portion 24 makes the intermediate surface 241 more hydrophilic than if the surface coating 24a were not provided.

In other words, the intermediate portion 24 has the surface coating 24a as a promoting structure that promotes the wetting and spreading of the condensed water Wc adhering to the intermediate portion 24 to the same extent or more than that of the evaporating portion 22. The surface coating 24a promotes wetting and spreading of the condensed water Wc more than when the surface coating 24a is not provided.

As described above, according to the present embodiment, the condensation section 20 is positioned below the evaporation section 22 and arranged so that the condensed water Wc generated in the evaporation section 22 flows down. Condensing section 20 has specific configuration 207 , and specific configuration 207 wets and spreads condensed water Wc that has flowed down to condensation section 20 in comparison with the case where specific configuration 207 is not provided. It's something that makes you laugh. Therefore, the condensed water Wc generated in the evaporating section 22 is easily pulled toward the condensing section 20 by the specific configuration 207 of the condensing section 20 . Therefore, the condensed water Wc is less likely to stay in the evaporating section 22 , and the condensed water Wc can be smoothly guided to the condensing section 20 .

In addition, since the condensed water Wc smoothly flows down without staying in the evaporating section 22, it is possible to prevent deterioration of the drainage performance in the evaporating section 22. As a result, for example, water splashing in the evaporating section 22 can be prevented. be.

In addition, the heat exchanger 10 is arranged in a posture inclined with respect to the vertical direction Dg as described above. Specifically, the upper side of the heat exchanger 10 is located upstream of the air flow passing through the condenser section 20 (in other words, upstream of the second air passage in which the condenser section 20 is arranged) with respect to the lower side. , the heat exchanger 10 is inclined with respect to the vertical direction Dg. In other words, the condensing section 20 and the evaporating section 22 of the heat exchanger 10 are each inclined with respect to the vertical direction Dg so that the air inflow surface 20b of the condensing section 20 into which the air flows faces obliquely downward.

Therefore, it is possible to apply gravity so that the condensed water Wc flowing down from the evaporating section 22 is biased toward the upstream side of the air flow in the condensing section 20 . This makes it easier for the condensed water Wc to spread in the condensing part 20 along with the air passing through the condensing part 20, making it possible to reduce the thickness of the condensed water Wc and promote the evaporation of the condensed water Wc.

(1) According to the present embodiment, the condensation section 20 has the surface coating 207a, which is a hydrophilic coating applied to the condensation section 20, as the specific configuration 207. The surface coating 207a of the condensing section 20 imparts the same hydrophilicity to the surface of the condensing section 20 as compared to the evaporating section 22, such that the surface of the condensing section 20 is more hydrophilic than if the surface coating 207a were not provided. Improves hydrophilicity. Therefore, the condensed water Wc flowing into the condensing section 20 is not stagnant due to the surface properties of the condensing section 20, and the condensed water Wc can flow in the condensing section 20 while being thinned.

In addition, since the condensed water Wc that has flowed down to the condenser 20 flows as a thin film, the heat exchange between the condensed water Wc and the refrigerant is efficiently performed in the condenser 20. For example, all of the condensed water that has flowed down to the condenser 20 It is easy to evaporate the water Wc. By evaporating all the condensed water Wc in this way, the performance of the condenser 20 is improved, and the remaining condensed water Wc that has not been evaporated in the condenser 20 is prevented from splashing. can be prevented from remaining as liquid in the condensation section 20 .

(2) Further, according to the present embodiment, the intermediate portion 24 is arranged in the middle of the path along which the condensed water Wc flows from the evaporating portion 22 to the condensing portion 20 . The intermediate portion 24 has a surface coating 24a as a promoting structure that promotes the wetting and spreading of the condensed water Wc adhering to the intermediate portion 24 to the same extent or more than that of the evaporating portion 22 . In addition, the surface coating 24a promotes wetting and spreading of the condensed water Wc more than when the surface coating 24a is not provided.

Therefore, it is possible to prevent the condensed water Wc from stagnation while flowing from the evaporating part 22 to the condensing part 20 , and allow the condensed water Wc to smoothly flow down from the evaporating part 22 to the condensing part 20 .

(3) In addition, according to the present embodiment, the surface coating 24 a of the intermediate section 24 gives the intermediate surface 241 the same hydrophilicity as compared to the evaporator section 22 . Also, the surface coating 24a of the intermediate portion 24 makes the intermediate surface 241 more hydrophilic than if the surface coating 24a were not provided.

Therefore, the condensed water Wc can be thinned and flowed. This prevents the condensed water Wc from stagnation while flowing from the evaporating section 22 to the condensing section 20 , and allows the condensed water Wc to smoothly flow down from the evaporating section 22 to the condensing section 20 .

(4) Further, according to the present embodiment, the plurality of evaporating tube portions 225 are configured integrally with the plurality of condensing tube portions 205, respectively. Therefore, it is possible to easily realize a structure in which the condensed water Wc generated in the evaporating section 22 easily flows down to the condensing tube section 205 and the condensing fins 206 of the condensing section 20 .

Also, it is easy to apply the same surface treatment to both the condensation section 20 and the evaporation section 22 . Therefore, the surface coatings 24a, 207a, and 227a applied to the heat exchanger 10 are all the same hydrophilic coating, and it is easy to make the hydrophilicity uniform in the condensation section 20, the evaporation section 22, and the intermediate section 24. .

(5) Further, according to the present embodiment, the surface coating 227a of the evaporating section 22 is a hydrophilic coating. Therefore, the surface coating 227a of the evaporating section 22 wets and spreads the condensed water Wc adhering to the surface of the evaporating section 22 in comparison with the case where the surface coating 227a is not provided. Corresponds to certain cooler configurations of the present disclosure that the evaporator section 22 has.

Since such a surface coating 227 a is applied to the surface of the evaporating section 22 , the condensed water Wc is less likely to stay in the evaporating section 22 , and the condensed water Wc can efficiently flow down to the condensing section 20 .

(Second embodiment)
Next, a second embodiment will be described. In this embodiment, differences from the above-described first embodiment will be mainly described. Also, the same or equivalent parts as those of the above-described embodiment will be omitted or simplified. This also applies to the description of the embodiments that will be described later.

As shown in FIGS. 8 and 9, in this embodiment, the condensation fins 206 have a plurality of fine grooves 206b formed on the surface of the condensation fins 206 as a specific configuration 207. FIG. The plurality of fine grooves 206b are fine grooves formed so as to increase the hydrophilicity of the surface of the condensation fins 206. As shown in FIG.

For example, each of the plurality of fine grooves 206b extends in a direction that intersects the heat exchanger width direction Dw, and is arranged side by side at predetermined intervals in the heat exchanger width direction Dw. Also, the plurality of fine grooves 206b are evenly provided on the entire surface of the condensation fins 206. As shown in FIG.

(1) As described above, according to this embodiment, the condensation fins 206 have a plurality of fine grooves 206b formed to increase the hydrophilicity of the surface of the condensation fins 206 as the specific configuration 207. . Therefore, as indicated by the dashed arrow in FIG. 10, the condensed water Wc adhering to the surface of the condensation tube portion 205 smoothly flows from the condensation tube portion 205 to the condensation fins 206, and the condensed water Wc flowing to the condensation fins 206 is It is led to the louver 206a while being thinned. Since the condensed water Wc exchanges heat with the refrigerant around the louver 206a, the heat exchange between the condensed water Wc and the refrigerant is efficiently performed in the condenser 20. For example, all the condensed water flowing down to the condenser 20 It is easy to evaporate Wc.

Except for what has been described above, this embodiment is the same as the first embodiment. In addition, in the present embodiment, it is possible to obtain the same effects as in the first embodiment, which are provided by the configuration common to that of the first embodiment.

Although the surface coatings 24a, 207a, and 227a are applied to the heat exchanger 10 in the first embodiment, the surface coatings 24a, 207a, and 227a may be applied to the heat exchanger 10 in the present embodiment. It may or may not be applied. Unless otherwise specified, this also applies to embodiments described later based on the first embodiment.

(Third embodiment)
Next, a third embodiment will be described. In this embodiment, differences from the above-described first embodiment will be mainly described.

In this embodiment, as shown in FIGS. 11 and 12, the intermediate section 24 of the heat exchanger 10 has a plurality of recessed sections 242 extending from the evaporating section 22 side to the condensing section 20 side. The recessed portion 242 is formed such that a cross section perpendicular to the direction in which the recessed portion 242 extends (specifically, the longitudinal direction Dv of the heat exchanger) has a recessed shape.

Specifically, the concave portion 242 extends continuously from the intermediate portion 24 to each of the condensation portion 20 and the evaporation portion 22 . In other words, as shown in FIGS. 11 to 13, the condensation section 20 has a condensation recessed portion 208 formed continuously in series from the recessed portion 242 of the intermediate portion 24 and having a concave cross section. there is The evaporating portion 22 has an evaporating concave portion 228 which is formed so as to continue in series from the concave portion 242 of the intermediate portion 24 and has a concave cross section. In addition, in the description of the present embodiment, the concave portion 242 of the intermediate portion 24 is also referred to as the intermediate concave portion 242 .

That is, the heat exchanger 10 includes a plurality of overall concave portions 39 each composed of a condensation concave portion 208 , an intermediate concave portion 242 and an evaporating concave portion 228 . Specifically, each of the plurality of overall concave portions 39 is provided at one edge portion of the laminated structure 38 in the heat exchanger width direction Dw. It extends in the heat exchanger longitudinal direction Dv to the lower part of the part 20 . Therefore, in the condenser section 20, the plurality of overall concave portions 39 are provided upstream of the air flow passing through the condenser section 20, and in the evaporator section 22, they are provided upstream of the air flow passing through the evaporator section 22. is provided.

Note that the condensation recessed portion 208 wets and spreads the condensed water Wc that has flowed down to the condensation portion 20 in comparison with the case where the condensation recessed portion 208 is not provided. 20 specific configurations 207 are provided. In addition, the evaporation recessed portion 228 wets and spreads the condensed water Wc along the evaporation recessed portion 228 in the evaporator 22 compared to the case where the evaporation recessed portion 228 is not provided. It corresponds to a certain cooler configuration.

A pair of overall recessed portions 39 are provided for each laminated structure 38 . One of the pair of overall concave portions 39 is formed by bending the edge of the first plate member 381 on one side in the heat exchanger width direction Dw toward one side in the stacking direction Ds. The other of the pair of overall concave portions 39 is formed by bending the edge of the second plate member 382 on one side in the heat exchanger width direction Dw toward the other side in the stacking direction Ds. there is

Therefore, as shown in FIG. 12, the cross-sectional concave shape of the intermediate concave portion 242 in the intermediate portion 24 is V-shaped, for example. Further, as shown in FIG. 13, in the portion of the condensation portion 20 in which the condensation recessed portion 208 and the convex shape of the condensation tube portion 205 are aligned in parallel, the cross-sectional shape of the condensation recessed portion 208 is changed by the coupling of the two. A certain concave shape is, for example, a U shape. This is the same for the evaporator 22 as well.

(1) As described above, according to the present embodiment, the intermediate portion 24 of the heat exchanger 10 has a plurality of concave portions 242 extending from the evaporating portion 22 side to the condensing portion 20 side. The recessed portion 242 of the intermediate portion 24 is formed so that the cross section perpendicular to the direction in which the recessed portion 242 extends has a recessed shape. Therefore, as shown in FIG. 12, it is possible to guide the condensed water Wc inside the recessed portion 242 of the intermediate portion 24 and lead it to the condensation portion 20 .

The recessed portion 242 of the intermediate portion 24 acts to wet and spread the condensed water Wc adhering to the intermediate portion 24 , so that the wetting and spreading of the condensed water Wc is the same as that of the evaporating portion 22 . It can be said that it is provided as a promotion configuration for promoting the above.

(2) Further, according to the present embodiment, as shown in FIG. 11, the concave portion 242 of the intermediate portion 24 extends continuously from the intermediate portion 24 to the condensation portion 20 and the evaporation portion 22 respectively. there is The condensation concave portion 208 formed by extending from the concave portion 242 of the intermediate portion 24 is provided upstream of the air flow passing through the condensation portion 20 in the condensation portion 20 .

Therefore, the condensed water Wc generated in the evaporating section 22 can be guided to the air flow upstream side of the condensing section 20 . This makes it easier for the condensed water Wc to spread in the condensing part 20 along with the air passing through the condensing part 20, making it possible to reduce the thickness of the condensed water Wc and promote the evaporation of the condensed water Wc. This means that the upper side of the heat exchanger 10 of the present embodiment is located on the upstream side of the air flow in the condenser section 20 (in other words, the upstream side of the second air passage) with respect to the lower side. This is particularly effective because the container 10 is inclined with respect to the vertical direction Dg.

Except for what has been described above, this embodiment is the same as the first embodiment. In addition, in the present embodiment, it is possible to obtain the same effects as in the first embodiment, which are provided by the configuration common to that of the first embodiment.

Although this embodiment is a modification based on the first embodiment, it is also possible to combine this embodiment with the above-described second embodiment.

(Fourth embodiment)
Next, a fourth embodiment will be described. In this embodiment, differences from the above-described first embodiment will be mainly described.

As shown in FIG. 14, a plurality of grooves 241a are formed in the intermediate surface 241 in this embodiment. The plurality of grooves 241a are longitudinal grooves extending in the vertical direction Dg. Specifically, the plurality of grooves 241a of the present embodiment are longitudinal grooves extending along the vertical direction Dg. 14 shows the intermediate surface 241 facing the other side in the stacking direction Ds, the plurality of grooves 241a are formed not only in the intermediate surface 241 facing the other side in the stacking direction Ds but also in the stacking direction. An intermediate surface 241 facing one side of Ds is also formed in the same manner as shown in FIG.

For example, in the present embodiment, the plurality of grooves 241a of the intermediate surface 241 may be distributed over the entire intermediate portion 24. It is provided so as to be unevenly distributed. Specifically, the plurality of grooves 241a of the intermediate surface 241 are provided on one side of the through hole 38a of the laminated structure 38 in the heat exchanger width direction Dw.

(1) As described above, according to this embodiment, the intermediate surface 241 is formed with a plurality of grooves 241a. As a result, the condensed water Wc adhering to the intermediate surface 241 spreads while permeating into the plurality of grooves 241a.

Since the plurality of grooves 241a of the intermediate surface 241 act to spread the condensed water Wc adhering to the intermediate surface 241, the wet spreading of the condensed water Wc is the same or larger than that of the evaporating section 22. It can be said that it is provided as a promotion configuration for further promotion.

(2) Further, according to the present embodiment, the plurality of grooves 241a formed in the intermediate surface 241 are vertical grooves extending in the vertical direction Dg. Therefore, the plurality of grooves 241a act to wet and spread the condensed water Wc adhering to the intermediate surface 241 in the vertical direction Dg. Therefore, the synergistic effect of the action of the plurality of grooves 241 a and the action of gravity can promote the flow of the condensed water Wc to the condensation section 20 . In this embodiment, the longitudinal grooves extending in the vertical direction Dg do not need to extend parallel to the vertical direction Dg, and may extend at an angle to the vertical direction Dg as long as they extend vertically.

Except for what has been described above, this embodiment is the same as the first embodiment. In addition, in the present embodiment, it is possible to obtain the same effects as in the first embodiment, which are provided by the configuration common to that of the first embodiment.

Although this embodiment is a modification based on the first embodiment, it is also possible to combine this embodiment with the above-described second or third embodiment.

(Fifth embodiment)
Next, a fifth embodiment will be described. In this embodiment, differences from the above-described fourth embodiment will be mainly described.

As shown in FIG. 15, in this embodiment, the plurality of grooves 241a formed in the intermediate surface 241 do not extend along the vertical direction Dg. The plurality of grooves 241a extend obliquely with respect to the vertical direction Dg. Although the plurality of grooves 241a of the intermediate surface 241 are inclined with respect to the vertical direction Dg, they still extend in the vertical direction Dg.

The plurality of grooves 241a are provided in a grid pattern. Therefore, the surface area of the intermediate surface 241 can be made larger than when the plurality of grooves 241a are simply arranged in parallel. can do.

Except for what has been described above, this embodiment is the same as the fourth embodiment. In addition, in the present embodiment, the same effects as in the fourth embodiment can be obtained from the configuration common to that of the fourth embodiment.

(Sixth embodiment)
Next, a sixth embodiment will be described. In this embodiment, differences from the above-described fourth embodiment will be mainly described.

As shown in FIG. 16, in this embodiment, a plurality of vertical grooves 241a are formed in an intermediate surface 241, as in the fourth embodiment. Further, in this embodiment, the condenser section 20 has a plurality of condensation section surface grooves 209 formed on the surface of the condenser tube section 205 as a specific feature 207 . In this respect, this embodiment differs from the fourth embodiment.

Specifically, the plurality of condensation section surface grooves 209 are formed not only on the surface of the condensation tube section 205 but also on the surface of the condensation section 20 around the first condensation tank forming section 202 . Also, the condensation portion surface grooves 209 are formed on both the surface of the condensation portion 20 on one side and the surface on the other side in the stacking direction Ds.

Also, some of the plurality of condensation portion surface grooves 209 are continuously connected to some of the plurality of grooves 241 a formed in the intermediate surface 241 . The groove shape of the condensation portion surface groove 209 is the same as the groove shape of the groove 241 a of the intermediate surface 241 . That is, the plurality of condensation portion surface grooves 209 are longitudinal grooves extending in the vertical direction Dg. Specifically, the plurality of condensation portion surface grooves 209 of this embodiment are longitudinal grooves extending along the vertical direction Dg.

For example, in the present embodiment, the plurality of condensation section surface grooves 209 may be distributed over the entire surface of the condensation section 20 . It is only provided around and on top of the condensation tube section 205 . This is because the condensed water Wc that has flowed down to the condensation section 20 first adheres to the surroundings of the first condensation tank forming section 202 and the upper portion of the condensation tube section 205 in the condensation section 20 .

(1) As described above, according to the present embodiment, the condensation section 20 has a plurality of condensation section surface grooves 209 formed on the surface of the condensation tube section 205 as the specific configuration 207 . As a result, the condensed water Wc adhering to the surface of the condensation tube portion 205 in which the condensation portion surface grooves 209 are formed spreads while permeating into the condensation portion surface grooves 209. It can flow smoothly.

(2) Further, according to the present embodiment, the plurality of condensation portion surface grooves 209 are longitudinal grooves extending in the vertical direction Dg. Therefore, the plurality of condensation portion surface grooves 209 act to wet and spread the condensed water Wc adhering to the surface on which the condensation portion surface grooves 209 are formed in the vertical direction Dg. Therefore, the synergistic effect of the action of the plurality of condensing section surface grooves 209 and the action of gravity can promote the flow and spread of the condensed water Wc on the surface of the condensing section 20 . In this embodiment, the longitudinal grooves extending in the vertical direction Dg do not need to extend parallel to the vertical direction Dg, and may extend at an angle to the vertical direction Dg as long as they extend vertically.

Except for what has been described above, this embodiment is the same as the fourth embodiment. In addition, in the present embodiment, the same effects as in the fourth embodiment can be obtained from the configuration common to that of the fourth embodiment.

(Seventh embodiment)
Next, a seventh embodiment will be described. In this embodiment, differences from the sixth embodiment described above will be mainly described.

As shown in FIG. 17, in the present embodiment, a plurality of condensation section surface grooves 209 formed on the surface of the condensation section 20 are provided in a lattice similar to the grooves 241a of the intermediate surface 241 shown in FIG. ing. Therefore, since the surface area of the condensation section 20 can be made larger than when the plurality of condensation section surface grooves 209 are simply arranged in parallel, the surface of the condensation section 20 can be made hydrophilic, and the surface of the condensation section 20 can be of water can be promoted.

Except for what has been described above, this embodiment is the same as the sixth embodiment. In addition, in the present embodiment, the same effects as in the sixth embodiment can be obtained from the same configuration as in the sixth embodiment.

(Eighth embodiment)
Next, an eighth embodiment will be described. In this embodiment, differences from the above-described first embodiment will be mainly described.

As shown in FIGS. 18 and 19, in this embodiment, the condensation section 20 and the evaporation section 22 are fixed to the one side plate section 30 and the other side plate section 32, respectively, but are not directly connected. do not have. The evaporating section 22 is spaced apart from the condensing section 20 in the longitudinal direction Dv of the heat exchanger.

Therefore, in this embodiment, the heat exchanger 10 does not have a configuration corresponding to the intermediate section 24 of the first embodiment. In addition, in this embodiment, surface coatings 207a and 227a are applied to the heat exchanger 10 in the same manner as in the first embodiment.

Except for what has been described above, this embodiment is the same as the first embodiment. In addition, in the present embodiment, it is possible to obtain the same effects as in the first embodiment, which are provided by the configuration common to that of the first embodiment.

Although this embodiment is a modification based on the first embodiment, it is also possible to combine this embodiment with any of the second, third, sixth, and seventh embodiments described above.

(Ninth embodiment)
Next, a ninth embodiment will be described. In this embodiment, differences from the eighth embodiment described above will be mainly described.

As shown in FIG. 20, in this embodiment, an intermediate portion 24 configured as a component separate from the condensation portion 20 and the evaporation portion 22 is inserted into the gap between the condensation portion 20 and the evaporation portion 22. there is As a result, the condenser section 20 and the evaporator section 22 are connected to each other in the longitudinal direction Dv of the heat exchanger via the intermediate section 24 . The intermediate portion 24 of the present embodiment has a function of promoting the flow of the condensed water Wc similarly to the intermediate portion 24 of the first embodiment. A surface coating 24a (see FIG. 7), which is a hydrophilic coating, is applied.

In addition, the surface of the intermediate portion 24 of the present embodiment is formed so as to be smoothly connected to the surface of the evaporating portion 22 and the surface of the condensing portion 20 without any step. This is to prevent the condensed water Wc from flowing from the evaporating portion 22 to the condensing portion 20 via the intermediate portion 24 .

For example, the intermediate part 24 may be configured as part of an air conditioning case that accommodates the heat exchanger 10 and forms a ventilation passage. Alternatively, the intermediate portion 24 may be configured as a component separate from the air conditioning case and housed in the air conditioning case together with the heat exchanger 10 .

A plurality of intermediate portions 24 are provided side by side in the stacking direction Ds (see FIG. 18). inserted in each.

Except for what has been described above, this embodiment is the same as the eighth embodiment. In addition, in the present embodiment, the same effects as in the eighth embodiment can be obtained from the configuration common to that of the eighth embodiment.

Further, since the intermediate portion 24 of the present embodiment corresponds to the intermediate portion 24 of the first embodiment, the effect of the intermediate portion 24, which is provided by the configuration common to that of the first embodiment, is the same as that of the first embodiment. The form can be obtained as well.

Although this embodiment is a modification based on the eighth embodiment, it is also possible to combine this embodiment with any of the above-described second to seventh embodiments.

(Other embodiments)
(1) In each of the above-described embodiments, as shown in FIGS. 3 and 4, for example, the heat exchanger 10 is arranged in a posture inclined with respect to the vertical direction Dg. may be placed in an upright position along the

(2) In the first embodiment described above, the same surface coating as the surface coating 207a of the condenser section 20 shown in FIGS. be. For example, it can be assumed that the evaporation section 22 is not provided with the surface coating 227a. In that case, the surface coating 207a of the condensing section 20 will also render the surface of the condensing section 20 more hydrophilic than the evaporator section 22. FIG.

It is also possible to assume that the evaporating section 22 is not provided with the surface coating 227a and the intermediate section 24 is provided with the surface coating 24a (see FIG. 7). In that case, the surface coating 24 a of the intermediate section 24 also renders the intermediate surface 241 more hydrophilic than the evaporator section 22 . That is, it can be said that the intermediate portion 24 is configured to promote the wetting and spreading of the condensed water Wc adhering to the intermediate portion 24 by the surface coating 24a more than the evaporating portion 22.

(3) In the second embodiment described above, as shown in FIG. 8, each of the plurality of fine grooves 206b provided in the condensation fin 206 extends in a direction intersecting the heat exchanger width direction Dw. Although they are arranged side by side at predetermined intervals in the exchanger width direction Dw, this is an example. For example, the plurality of fine grooves 206b may be provided in a grid pattern, or may be formed on the surface of the condensation fins 206 so as to extend curvedly.

(4) In the third embodiment described above, as shown in FIG. The inclusion of contoured portion 39 is an example. For example, it is conceivable that in heat exchanger 10 intermediate recess 242 is provided, but one or both of condensing recess 208 and evaporating recess 228 are not provided.

(5) In the sixth embodiment described above, as shown in FIG. 16, not only the plurality of condensation section surface grooves 209 of the condensation section 20 but also the plurality of grooves 241a formed in the intermediate surface 241 are provided. , the plurality of grooves 241a on the intermediate surface 241 thereof may be omitted.

(6) In each of the above-described embodiments, as shown in FIGS. 1 and 2, the heat exchanger 10, the pressure reducing device 15, and the accumulator 16 are configured as separate devices, but this is an example. For example, as shown in FIG. 21, the heat exchanger 10, decompression device 15, and accumulator 16 may be integrated. Although the decompression device 15 shown in FIG. 21 is a capillary tube, the type of the decompression device 15 is not limited.

(7) In the first embodiment described above, as shown in FIGS. The shape of 24 is not limited. For example, Patent Document 1 discloses a tubular member in which a water conduit is formed to guide condensed water from an evaporator corresponding to the evaporating section 22 to a condenser corresponding to the condensing section 20. Intermediate section 24 may be such a tubular member. In that case, the inner wall surface of the tubular member facing the water conduit corresponds to the intermediate surface 241, and for example, the inner wall surface of the tubular member is coated with a hydrophilic coating.

(8) In the first embodiment described above, the surface coating 227a applied to the surface of the evaporator section 22 corresponds to a certain cooler configuration of the present disclosure, and in the third embodiment, the evaporative concave section 228 corresponds to the certain cooler configuration of the present disclosure. These are examples only. For example, when a plurality of fine grooves corresponding to the plurality of fine grooves 206b (see FIG. 8) provided in the condensation fins 206 of the second embodiment are provided on the surface of the evaporator 22, the evaporator 22 corresponds to certain cooler configurations of the present disclosure.

(9) In the above-described first and ninth embodiments, as shown in FIGS. 4 and 20, the position of the condenser section 20 and the position of the evaporator section 22 in the heat exchanger width direction Dw are aligned with each other. Although the condensation section 20 and the evaporation section 22 are arranged side by side, this is an example. For example, as shown in FIGS. 22 and 23, the condensation section 20 and the evaporation section 22 are arranged side by side so that the positions of the condensation section 20 and the evaporation section 22 in the width direction Dw of the heat exchanger are shifted from each other. It doesn't matter if it is. 22 and 23, the condensation section 20 and the evaporation section 22 are not inclined with respect to the vertical direction Dg, but are oriented along the vertical direction Dg.

(10) It should be noted that the present disclosure is not limited to the above-described embodiments, and can be implemented in various modifications. Moreover, the above-described embodiments are not unrelated to each other, and can be appropriately combined unless the combination is clearly impossible.

Further, in each of the above-described embodiments, it goes without saying that the elements constituting the embodiment are not necessarily essential, unless it is explicitly stated that they are essential, or they are clearly considered essential in principle. stomach. In addition, in each of the above-described embodiments, when numerical values such as the number, numerical value, amount, range, etc. of the constituent elements of the embodiment are mentioned, when it is explicitly stated that they are particularly essential, and when they are clearly limited to a specific number in principle It is not limited to that specific number, except when In addition, in each of the above-described embodiments, when referring to the material, shape, positional relationship, etc. of the constituent elements, unless otherwise specified or in principle limited to a specific material, shape, positional relationship, etc. , its material, shape, positional relationship, and the like.

Claims (14)

1. A heat exchange system for exchanging heat between a refrigerant and air,
   a cooler (22) that cools the air with a refrigerant;
   A radiator ( 20) and
   The heat exchange system, wherein the specific configuration causes the condensed water that has flowed down to the radiator to wet and spread more than when the specific configuration is not provided.
2. The radiator has a surface coating (207a) applied to the radiator as the specific configuration,
   The surface coating of the radiator imparts the same or greater hydrophilicity to the surface of the radiator as compared to the cooler than if the surface coating of the radiator were not provided. 2. The heat exchange system of claim 1, wherein also enhances the hydrophilicity of the surface of the radiator.
3. The radiator has radiator fins (206) arranged in a ventilation space (20a) through which air passes in the radiator,
   The heat exchange system according to claim 1 or 2, wherein the radiator fins have, as the specific configuration, a plurality of fine grooves (206b) formed to increase the hydrophilicity of the surfaces of the radiator fins. .
4. an intermediate portion (24) provided between the cooler and the radiator and located in the middle of the flow of the condensed water from the cooler to the radiator;
   the intermediate portion has an facilitating configuration (24a, 241a, 242) that promotes the wetting and spreading of the condensed water as much or more than the cooler;
   4. A heat exchange system according to any one of the preceding claims, wherein the facilitating arrangement facilitates the spreading of the condensate more than if the facilitating arrangement were not provided.
5. an intermediate portion (24) provided between the cooler and the radiator and having an intermediate surface (241) disposed in the middle of the flow of the condensed water from the cooler to the radiator;
   said intermediate portion having a surface coating (24a) applied to said intermediate surface;
   The surface coating of the intermediate section imparts the same or greater hydrophilicity to the intermediate surface as compared to the cooler, and the surface coating of the intermediate section is more hydrophilic than if the surface coating of the intermediate section were not provided. 4. A heat exchange system according to any one of claims 1 to 3, which improves the hydrophilicity of the intermediate surface.
6. an intermediate portion (24) provided between the cooler and the radiator and located in the middle of the flow of the condensed water from the cooler to the radiator;
   the intermediate portion has a concave portion (242) extending from the cooler side to the radiator side;
   4. The heat exchange system according to any one of claims 1 to 3, wherein said concave portion is formed so that a cross section perpendicular to a direction in which said concave portion extends has a concave shape.
7. 7. The heat sink of claim 6, wherein the concave portion extends continuously to each of the cooler and the radiator, and in the radiator is provided upstream of air flow passing through the radiator. exchange system.
8. an intermediate portion (24) provided between the cooler and the radiator and having an intermediate surface (241) disposed in the middle of the flow of the condensed water from the cooler to the radiator;
   The heat exchange system according to any one of claims 1 to 3, wherein the intermediate surface is formed with a plurality of grooves (241a).
9. The heat exchange system according to claim 8, wherein the plurality of grooves formed in the intermediate surface include vertical grooves extending in the vertical direction (Dg).
10. The radiator has a radiator tube (205) through which a refrigerant flows,
    10. The heat exchange system according to any one of claims 1 to 9, wherein the radiator has, as the specific configuration, a plurality of grooves (209) formed on the surface of the radiator tube.
11. The heat exchange system according to claim 10, wherein the plurality of grooves formed on the surface of the radiator tube include vertical grooves extending in the vertical direction (Dg).
12. A plurality of the radiator tubes are provided,
    the cooler has a plurality of cooler tubes (225) through which a refrigerant flows;
    12. A heat exchange system according to claim 10 or 11, wherein the plurality of cooler tubes are integrally formed with the plurality of radiator tubes respectively.
13. the cooler has a plurality of cooler tubes (225) through which a refrigerant flows;
    The radiator has a plurality of radiator tubes (205) through which a refrigerant flows,
    10. The heat exchange system of any one of claims 1 to 9, wherein a plurality of said cooler tubes are integrally formed with a plurality of said radiator tubes respectively.
14. said cooler has a cooler configuration (227a, 228);
    14. Any one of claims 1 to 13, wherein the certain cooler arrangement allows the condensed water to spread over the cooler compared to when the certain cooler arrangement is not provided. The heat exchange system according to .

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