JP7406297B2 - Heat exchanger - Google Patents

Description

Regarding heat exchangers.

Some heat exchangers used in air conditioners etc. have a small diameter heat exchanger tube unit formed by bonding heat transfer fin plates (for example, Patent Document 1 (Japanese Patent Laid-Open No. 2006-90636) Public bulletin), etc.).

When a heat exchanger is used as an evaporator in a low-temperature environment, frost formation may occur locally due to the internal heat flux distribution. Air passage blockage may occur at locations where frost is concentrated, and the performance of the heat exchanger may deteriorate.

In the heat exchanger according to the first aspect, a plurality of heat transfer flow path sections and a plurality of heat transfer auxiliary sections extending in a first direction are formed in line in a second direction that is inclined or orthogonal to the first direction. The heat transfer unit has a plurality of heat transfer units arranged in a third direction different from both the first direction and the second direction.

Moreover, in the heat exchanger of the first aspect, the heat transfer unit is divided into a windward region and a leeward region along the second direction. When the heat exchanger of the first aspect is used as an evaporator, the refrigerant is allowed to flow into the heat transfer channel section arranged in the upwind region, and then the refrigerant is introduced into the heat transfer channel section arranged in the leeward region. Let it flow out. With such a configuration, the heat exchange performance of the entire heat exchanger can be optimized.

The heat exchanger according to the second aspect is the heat exchanger according to the first aspect, in which the number of heat transfer passage sections arranged in the leeward region is greater than the number of heat transfer passage sections arranged in the windward region. There are many. With such a configuration, optimal heat exchange can be achieved while suppressing frost formation.

The heat exchanger according to the third aspect is the heat exchanger according to the first aspect or the second aspect, and further includes a pressure reduction mechanism that reduces the pressure of the refrigerant. In addition, the heat exchanger according to the third aspect allows the refrigerant to flow from the heat transfer channel section disposed in the windward region to the heat transfer channel section disposed in the leeward region via the pressure reduction mechanism. With such a configuration, frost formation can be further suppressed.

In the heat exchanger according to the fourth aspect, the heat exchanger according to the first aspect to the third aspect is connected to the heat transfer unit from above and below along the first direction, and forms part of a refrigerant flow path. It further includes an upper header and a lower header. With such a configuration, it is possible to realize a heat exchanger in which condensed water can be easily discharged.

The heat exchanger according to the fifth aspect is the heat exchanger according to the fourth aspect, in which the windward region and the leeward region are formed by a partition member disposed inside the upper header and/or the lower header. be. Therefore, the windward region and the leeward region can be easily formed.

In the heat exchanger according to the sixth aspect, in the heat exchanger according to the first to fifth aspects, each heat transfer unit has at least 8 or more heat transfer flow path sections, and at least 2 or more heat transfer flow path sections. is placed in the windward area. Such a configuration allows optimization of heat exchange performance.

The heat exchanger according to the seventh aspect is the heat exchanger according to the first to sixth aspects, in which a heat insulating material is applied to the end of the heat transfer unit in the second direction when viewed in the first direction. Therefore, a decrease in temperature at the end can be suppressed.

The heat exchanger according to the eighth aspect is the heat exchanger according to the seventh aspect, in which the heat transfer unit has a first transfer unit, which is one of the heat transfer auxiliary parts, at an end in the second direction when viewed in the first direction. A heat auxiliary portion is formed. Moreover, the first heat transfer auxiliary part has a closed shape. Thereby, drainage performance during defrosting operation can be improved.

The air conditioner according to the ninth aspect is equipped with the heat exchangers according to the first to eighth aspects.

FIG. 1 is a schematic diagram showing the concept of a heat exchanger 10 according to an embodiment. It is a schematic diagram showing the composition of heat exchanger 10 concerning the same embodiment. FIG. 2 is a schematic diagram showing a cross-sectional shape of a first header 21 according to the same embodiment. FIG. 2 is a schematic diagram showing a cross-sectional shape of a second header 22 according to the same embodiment. It is a schematic diagram showing the composition of heat transfer unit 30 concerning the same embodiment. FIG. 3 is a schematic diagram for explaining the configuration of a heat transfer unit 30 according to the same embodiment. FIG. 2 is a schematic diagram for explaining the configuration of a heat transfer unit group 15 according to the same embodiment. It is a schematic diagram showing the cross-sectional shape of the heat exchanger 10 according to the same embodiment. FIG. 3 is a diagram for explaining a refrigerant flow path of the heat exchanger 10 according to the same embodiment. FIG. 3 is a diagram for explaining a refrigerant flow path of the heat exchanger 10 according to the same embodiment. It is a schematic diagram showing the composition of heat exchanger 10Z for comparison. 7 is a diagram for explaining a refrigerant flow path of a heat exchanger 10 according to modification A. FIG. 7 is a diagram for explaining a refrigerant flow path of a heat exchanger 10Y according to modification B. FIG. 7 is a schematic diagram for explaining the configuration of a heat transfer unit group 15 according to modification C. FIG. 7 is a schematic diagram for explaining the configuration of a heat transfer unit group 15 according to modification C. FIG. 7 is a schematic diagram for explaining the configuration of a heat transfer unit group 15 according to modification E. FIG. 16 is a schematic diagram for explaining the configuration of a heat transfer unit group 15 according to modification E (a partially enlarged view of FIG. 16). FIG. 7 is a schematic diagram for explaining the configuration of a heat transfer unit group 15 according to modification F. FIG. 19 is a schematic diagram for explaining the configuration of a heat transfer unit group 15 according to modification F (a partially enlarged view of FIG. 18). FIG. 7 is a schematic diagram for explaining a heat transfer unit group 15 according to modification example G. FIG. 7 is a schematic diagram for explaining a heat transfer unit group 15 according to modification example G. FIG. 7 is a schematic diagram for explaining the configuration of a heat transfer unit group 15 according to modification example H. FIG.

(1) Overview of Heat Exchanger The heat exchanger 10 exchanges heat between a fluid flowing inside and air flowing outside. Specifically, as conceptually shown in FIG. 1, the heat exchanger 10 is equipped with a first pipe 41 and a second pipe 42 through which refrigerant flows in and out. Further, a fan 6 for blowing air to the heat exchanger 10 is arranged near the heat exchanger 10. The fan 6 generates an air flow toward the heat exchanger 10, and as the air flow passes through the heat exchanger 10, heat is exchanged between the heat exchanger 10 and the air. Note that the heat exchanger 10 functions both as an evaporator that removes heat from the air and as a condenser (radiator) that releases heat to the air, and can be installed in an air conditioner or the like.

(2) Details of heat exchanger (2-1) Overall configuration As shown in FIG. 2, the heat exchanger 10 includes a heat transfer unit group 15, a first header 21, and a second header 22.

The heat transfer unit group 15 is composed of a plurality of heat transfer units 30. Further, the heat transfer unit group 15 is arranged such that the direction of the airflow generated by the fan 6 passes between each heat transfer unit 30. Details regarding the arrangement of each member will be described later.

(2-2) Header As shown in FIG. 3, the first header 21 is composed of a hollow member, and is configured to allow refrigerant in gas, liquid, and gas-liquid two-phase states to flow therethrough. . The first header 21 is connected to the heat transfer unit 30 above the heat transfer unit 30 . Furthermore, a connection surface 21S for connecting to the heat transfer unit 30 is formed on the lower surface of the first header 21. A connecting hole into which an end portion 31e of a heat transfer channel portion 31 described later is inserted is formed in the connecting surface 21S. Note that FIG. 3 shows the cross-sectional shape of the first header 21 when viewed from the third direction D3. The definition of the third direction D3 will be described later.

The second header 22 is connected to the first pipe 41 and the second pipe 42 and the heat transfer unit 30 below the heat transfer unit 30, and is connected between the first pipe 41 and the second pipe 42 and the heat transfer unit 30. This allows for the inflow and outflow of refrigerant. The second header 22 is made of a hollow member like the first header 21, and is configured to allow refrigerant in two phases of gas, liquid, and gas-liquid to flow therethrough. However, as shown in FIG. 4, the second header 22 has a partition member 22p that partitions the inside along the third direction D3. In the example of FIG. 4, for convenience, it is assumed that the second header 22 is divided into a windward second header 22U and a leeward second header 22L by a partition member 22p. The windward second header 22U and the leeward second header 22L are connected to the second header 22 and the first header 21, respectively. Note that the partition member 22p may be formed integrally with the second header 22, or may be constituted by a separate object. Furthermore, a connection surface 22S for connecting to the heat transfer unit 30 is formed on the upper surface of the second header 22. A connecting hole into which an end portion 31e of a heat transfer channel portion 31 described later is inserted is formed in the connecting surface 22S. Note that FIG. 4 shows the cross-sectional shape of the second header 22 when viewed from the third direction D3. The definition of the third direction D3 will be described later.

(2-3) Heat transfer unit (2-3-1)
As shown in FIG. 5, the heat transfer unit 30 includes a plurality of heat transfer channel sections 31 and a plurality of heat transfer auxiliary sections 32 extending in a "first direction D1" that are inclined or orthogonal to the first direction D1. They are formed in parallel in the second direction D2. Here, the heat transfer channel portion 31 has a substantially cylindrical shape, and the heat transfer auxiliary portion 32 has a substantially flat plate shape. Moreover, as shown in FIG. 6, the heat transfer channel portions 31 are formed so as to be lined up at a predetermined pitch PP in the second direction D2. By arranging a plurality of such heat transfer units 30 in a "third direction D3" that is different from both the first direction D1 and the second direction D2, a heat transfer unit group 15 as shown in FIG. It is formed. Here, in the heat transfer unit group 15, at least three or more heat transfer units 30 are arranged in a stacked manner.

For convenience of explanation, it is assumed that the first direction D1, the second direction D2, and the third direction D3 are orthogonal to each other. However, even if these directions D1 to D3 are not completely orthogonal, as long as they are inclined to each other, it is possible to realize the heat exchanger 10 according to the present embodiment.

The heat transfer unit 30 is connected to the first header 21 and the second header 22 at connection surfaces 21S and 22S of the first header 21 and the second header 22. Specifically, at the end of the heat transfer unit 30 in the first direction D1, as shown in FIG. 5, an end 31e of the heat transfer channel section 31 protrudes from an end 32e of the heat transfer auxiliary section 32. The end portion 31e of the heat transfer channel portion 31 is inserted into a connecting hole provided in the connecting surfaces 21S and 22S of the first header 21 and the second header 22. Then, the heat transfer unit 30 is fixed between the first header 21 and the second header 22 by brazing or the like at this connection point (see FIG. 8).

The heat transfer channel portion 31 allows the refrigerant to move between the first header 21 and the second header 22. Specifically, a substantially cylindrical passage is formed inside the heat transfer channel portion 31, and the refrigerant moves within this passage. Note that the heat transfer channel portion 31 according to the present embodiment is formed linearly along the first direction D1.

The heat transfer auxiliary section 32 promotes heat exchange between the refrigerant flowing inside the adjacent heat transfer channel section 31 and the surrounding air. Here, the heat transfer auxiliary section 32 is formed to extend in the first direction D1 similarly to the heat transfer channel section 31, and is arranged so as to be in contact with the adjacent heat transfer channel section 31. The heat transfer auxiliary section 32 may be formed integrally with the heat transfer channel section 31, or may be formed separately.

(2-3-2)
At least eight or more heat transfer channel sections 31 are formed in the heat transfer unit 30 according to the present embodiment. At least two or more heat transfer channel sections 31 are arranged in the windward region.

An example of such a configuration is shown in FIG. 8. Here, ten heat transfer channel portions 31 are formed in one heat transfer unit 30. Furthermore, the inside of the second header 22 is divided by a partition member 22p into a windward second header 22U arranged in the windward region WU and a leeward second header 22L arranged in the leeward region WL. Three heat transfer channel sections 31U are connected to the windward second header 22U, and seven heat transfer channel sections 31L are connected to the leeward second header 22L. Further, a heat transfer auxiliary portion 32g is formed at the windward end of the heat transfer unit 30. Note that FIG. 8 is a schematic diagram showing a cross-sectional shape of the heat exchanger 10 when viewed from the third direction D3.

(2-4) Refrigerant flow path When the heat exchanger 10 is used as an evaporator, the air flow W generated by the fan 6 flows along the second direction D2 as shown in FIG. In this state, liquid-phase refrigerant F flows into the heat exchanger 10 from the second pipe 42 . Subsequently, the refrigerant F flows into the upwind second header 22U from the second pipe 42. As shown in FIG. 10, the refrigerant F flows from below to above via the heat transfer passage section 31U connected to the windward second header 22U. Next, the refrigerant F flows into the second leeward header 22L via the heat transfer passage section 31L connected to the first header 21 and the second leeward header 22L. The refrigerant F exchanges heat with the air flow W while flowing through the heat transfer flow path portions 31U and 31L. As a result, the refrigerant F evaporates and changes into a gas phase. Then, the gas phase refrigerant F flows out from the first pipe 41. Note that FIG. 10 shows the state when the heat transfer unit 30 is viewed from the third direction D3.

When the heat exchanger 10 is used as a condenser, the refrigerant F flows in the opposite direction to that when it is used as an evaporator. That is, the gas phase refrigerant F flows in from the first pipe 41, and the liquid phase refrigerant F flows out from the second pipe 42.

(3) Method for manufacturing heat exchanger 10 Heat transfer unit 30 is manufactured from a metal material such as aluminum or aluminum alloy, for example. Specifically, first, a metal material is extruded using a mold having a cross-sectional shape as shown in FIG. 5, and the heat transfer channel portion 31 and the heat transfer auxiliary portion 32 are integrally formed. Subsequently, a portion of the heat transfer auxiliary portion 32 is cut out to provide a cutout portion 33. The cutout portion 33 is formed by, for example, cutting out a plurality of locations of the heat transfer auxiliary portion 32 by punching.

The first header 21 and the second header 22 are manufactured by processing a metal material into a tubular shape. The first header 21 and the second header 22 are provided with a connecting hole into which the end 31e of the heat transfer channel portion 31 is inserted. The connecting hole is a circular through hole formed by, for example, a drill.

To assemble the heat exchanger 10, the end portion 31e of the heat transfer channel portion 31 of the heat transfer unit 30 is inserted into the connection hole of the first header 21 and the second header 22. Thereby, the end portion 32e of the heat transfer auxiliary portion 32 comes into contact with the connection surfaces 21S and 22S of the first header 21 and the second header 22. At this contact location, the heat transfer unit 30, the first header 21, and the second header 22 are fixed by brazing or the like.

(4) Features (4-1)
As explained above, in the heat exchanger 10 according to the present embodiment, the plurality of heat transfer flow path sections 31 and the plurality of heat transfer auxiliary sections 32 extending in the first direction D1 are inclined or perpendicular to the first direction D1. It has heat transfer units 30 formed in line in the second direction D2. Here, a plurality of heat transfer units 30 are arranged in a third direction D3 that is different from both the first direction D1 and the second direction D2, and form a heat transfer unit group 15.

Furthermore, in the heat exchanger 10 according to the present embodiment, the heat transfer unit 30 is divided into a windward region WU and a leeward region WL along the second direction D2. When the heat exchanger 10 is used as an evaporator, the refrigerant F flows into the heat transfer channel section 31U disposed in the windward region WU, and then the heat transfer channel section 31L disposed in the leeward region WL. Let refrigerant F flow out.

In short, in the heat exchanger 10 according to the present embodiment, the refrigerant flow path is turned back at least once in the second direction D2 in which the air flow W occurs. Thereby, a heat exchanger with excellent heat exchange performance can be provided.

Supplementally, as shown in FIG. 11, for example, in a heat exchanger 10Z in which the refrigerant F is caused to flow once from below to above along the first direction D1 through the heat transfer unit 30Z, the temperature is low (for example, 7 degrees Celsius). When used as an evaporator in the environment described below), frost may form between the heat transfer units 30Z because the amount of heat transferred in the windward side heat transfer channel portion is large. Furthermore, air passage blockage may occur due to frost formation. Note that no partition member or the like is provided inside the first header 21Z and the second header 22Z shown in FIG.

In contrast, in the configuration of the heat exchanger 10 according to the present embodiment, the number of channels for the refrigerant F flowing in from the second pipe 42 is limited to the number of the upwind heat transfer channel sections 31U, so that the refrigerant pressure There will be a loss. Then, due to this pressure loss, the refrigerant temperature in the windward heat transfer channel section 31U increases. Therefore, when the heat exchanger 10 is used as an evaporator, the amount of heat exchanged in the upwind heat transfer channel section 31U is suppressed. Thereby, fluctuations in heat flux depending on the position within the heat transfer unit group 15 can be suppressed. As a result, when the heat exchanger 10 is used as an evaporator in a low-temperature environment (for example, 7 degrees Celsius or lower), local frost formation can be avoided, resulting in a heat exchanger with excellent heat exchange performance. equipment can be provided.

Furthermore, in the heat exchanger 10Z having the configuration shown in FIG. 11, due to the leading edge effect of the heat transfer assisting section on the windward side, the amount of heat exchanged in the heat transfer channel section on the windward side is greater than that in the heat transfer channel section on the leeward side. The amount of heat exchanged is large compared to the amount of heat exchanged. Therefore, when the refrigerant F flowing in from the second pipe 42 is caused to flow through a plurality of heat transfer flow path sections, the refrigerant F may completely evaporate in the heat transfer flow path section on the windward side. As a result, a situation may arise in which sufficient heat exchange is not performed in the heat exchanger 10Z.

On the other hand, in the configuration of the heat exchanger 10 according to the present embodiment, all of the refrigerant F flowing from the second pipe 42 is once flowed to the windward side heat transfer passage section 31U, so that the windward side heat transfer passage section It is possible to avoid a situation where the refrigerant completely evaporates with 31U. As a result, the heat exchange performance of the heat exchanger 10 can be optimized.

(4-2)
Further, in the heat exchanger 10 according to the present embodiment, the number of heat transfer passage sections 31L arranged in the leeward region WL is greater than the number of heat transfer channel sections 31U arranged in the windward region WU. be. Furthermore, each heat transfer unit 30 has at least eight or more heat transfer flow path sections 31, and at least two or more heat transfer flow path sections 31U are arranged in the windward region WU. With such a configuration, when the heat exchanger 10 is used as an evaporator in a low temperature environment (for example, 7 degrees Celsius or less), optimal heat exchange can be achieved while suppressing frost formation.

(4-3)
The heat exchanger 10 according to the present embodiment also includes a first header 21 (upper header) and a second header that are connected to the heat transfer unit 30 from above and below along the first direction D1 and form a part of the refrigerant flow path. It further includes a header 22 (lower header). With such a configuration, the longitudinal direction of the heat transfer unit 30 can be oriented vertically, and attached water (such as dew water) can be easily discharged. Furthermore, ease of assembly and workability can be improved.

However, the heat exchanger 10 according to the present embodiment does not exclude a configuration in which the first header 21 and the second header 22 are provided in the horizontal direction instead of in the vertical direction.

(4-4)
Further, in the heat exchanger 10 according to the present embodiment, the windward region WU and the leeward region WL are formed by a partition member 22p arranged inside the second header 22 (lower header). Therefore, the windward region WU and the leeward region WL can be easily formed without performing any special processing on the heat transfer unit 30.

Note that in the heat exchanger 10 according to the present embodiment, a partition member may be provided inside the first header 21 instead of the second header 22 depending on the flow path of the refrigerant. Alternatively, a partition member may be provided in both the first header 21 and the second header 22 depending on the flow path of the refrigerant.

(4-5)
Further, in the heat exchanger 10 according to the present embodiment, each heat transfer unit 30 can be formed from a single member by extrusion molding of a metal material. Furthermore, a plurality of cutouts 33 can be formed at once by punching. Therefore, it is possible to provide the heat exchanger 10 with high assemblability and workability.

(5) Modification (5-1) Modification A
The heat exchanger 10 according to this embodiment may further include a pressure reduction mechanism that reduces the pressure of the refrigerant. Specifically, as conceptually shown in FIG. 12, the heat exchanger 10 has a refrigerant flow path (heat transfer flow path section 31U) in an upwind region WU and a refrigerant flow path (heat transfer flow path section 31L) in a leeward region WL. A pressure reducing mechanism 25 constituted by an electric valve or the like may be provided between the two. By expanding the refrigerant F using the decompression mechanism 25, the refrigerant temperature in the windward region can be optimized. As a result, when the heat exchanger 10 is used as an evaporator in a low temperature environment (for example, 7 degrees Celsius or lower), the occurrence of frost can be further suppressed.

(5-2) Modification B
The heat exchanger 10 according to this embodiment is not limited to the above configuration. That is, the heat exchanger 10 according to the present embodiment can adopt any form as long as the refrigerant flow path is turned back at least once in the second direction D2 in which the air flow W is generated. For example, a heat exchanger 10Y having a configuration having a refrigerant flow path as shown in FIG. 13 may be used. Note that FIG. 13 is a schematic diagram for explaining the refrigerant flow path formed inside the heat exchanger 10Y.

In the example shown in FIG. 13, a partition member 22ps is provided inside the windward second header 22U along the second direction D2 near the center of the windward second header 22U. Thereby, the windward second header 22U is divided into two regions: the windward upstream second header 22UA and the windward downstream second header 22UB. Further, in the example shown in FIG. 13, a partition member 21p etc. are provided inside the first header 21, and the first header 21 is connected to the windward first header 21U and the leeward first header along the second direction D2. It is divided into a header 21L. In the heat exchanger 10Y having such a configuration, the refrigerant F that has flowed from the second pipe 42 into the second windward header 22UA passes through the heat transfer channel section in the windward upstream region, and then flows into the windward first header 22UA. It flows into 21U. Subsequently, the refrigerant F flows into the heat transfer channel section in the windward downstream region via the windward first header 21U. Then, the refrigerant that has flowed into the windward downstream second header 22UB flows into the leeward second header 22L via a connecting pipe (not shown) or the like. The refrigerant F that has flowed into the second leeward header 22L is discharged into the first pipe 41 via the first leeward header 21L. In addition, in the heat exchanger 10Y, the first pipe 41 is connected to the leeward first header 21L.

Even in the heat exchanger 10Y having such a configuration, the refrigerant flow path is turned back at least once in the second direction D2 in which the airflow W occurs, so the same effect as described above can be achieved. .

(5-3) Modification C
In addition, the heat exchanger 10 according to the present embodiment has a heat insulating material I at the windward end of the heat transfer unit 30 in the second direction D2 (here, the heat transfer auxiliary part 32g) when viewed from the first direction D1. may be applied (see FIGS. 14 and 15). Thereby, a decrease in temperature at the end can be suppressed. As a result, when the heat exchanger 10 is used as an evaporator in a low temperature environment (for example, 7 degrees Celsius or lower), frost formation can be suppressed, and air passage blockage can be avoided or delayed.

In addition, in the example shown in FIGS. 14 and 15, the above-mentioned end portion of the heat transfer unit 30 is the heat transfer auxiliary portion 32g. Furthermore, this windwardmost heat transfer auxiliary part 32g (first heat transfer auxiliary part) has a closed shape. Here, the "closed shape" refers to a flat shape without holes, cuts, etc. Thereby, drainage performance during defrosting operation can be further improved.

As a supplementary note, if holes, notches, etc. are formed in the heat transfer auxiliary portion 32g, water generated by melting frost may be retained in the holes, notches, etc. In that case, the area where water is retained may become the starting point for the next frost formation. On the other hand, in the heat exchanger 10 according to modification C, the heat transfer auxiliary portion 32g has a shape without holes, cuts, etc., so that frost formation that occurs after the defrosting operation can be suppressed.

(5-4) Modification D
Further, the heat transfer channel portion 31 according to the present embodiment is not limited to the one described above, and may have other forms. For example, the cross-sectional shape of the heat transfer channel portion 31 when viewed from the first direction D1 is one of a semicircular shape, an elliptical shape, a flattened shape, an upper half shape of an airfoil, and/or a lower half shape of an airfoil. or any combination thereof. In short, the heat exchanger 10 can adopt a shape that optimizes heat exchange performance.

(5-5) Modification E
Moreover, the heat transfer unit group 15 according to this embodiment may have a form as shown in FIGS. 16 and 17. Note that FIG. 17 is a partially enlarged view of FIG. 16 (corresponding to the dotted line portion in FIG. 16).

In the example shown in FIGS. 16 and 17, the heat transfer unit 30 (including 30a, 30b, and 30c) swells at the first position L1 (including L1a, L1b, and L1c) in the second direction D2, and the heat transfer channel portion The first bulging portion 31p (including 31pa, 31pb, and 31pc) forming the first bulging portion 31 and the first flat portion 31q formed at the first position L1 in the opposite direction to the direction in which the first bulging portion 31p is formed. (including 31qa, 31qb, and 31qc). In addition, in modification E, the "first position" is defined for each heat transfer unit, and the first position L1a of the heat transfer unit 30a is different from the first positions L1b and L1c of the heat transfer units 30b and 30c. means location.

In addition, at least one heat transfer unit 30a is adjacent to the heat transfer unit 30b on one side, and the surface on which the first bulge 31pa is formed and the first bulge 31pb of the adjacent heat transfer unit 30b. The surface on which the surface is formed faces the opposite direction. Further, the heat transfer unit 30a is different from the adjacent other heat transfer unit 30c on the other side by the surface where the first plane portion 31qa is formed and the surface where the first plane portion 31qc of the other heat transfer unit 30c is formed. It is arranged in such a way that the surface facing the

With such a configuration, when the heat exchanger 10 is used as an evaporator, the air flow passes through the air passage where the first plane parts 31qa, 31qc, etc. face each other, so the amount of frost formation is suppressed. be able to. Thereby, heat exchange performance can be improved depending on the usage environment.

Note that in the air passage where the first bulging portions 31pa and 31pb face each other, contraction of the air flow occurs, and frost formation tends to occur intensively in the air passage. However, even if such frosting occurs, depending on the usage environment, the heat exchanger may be different from the heat exchanger in which almost identical bulges are formed on both sides of the heat transfer unit as shown in Figure 7. Therefore, the heat exchange performance of the entire heat exchanger can be improved.

Moreover, as shown in FIG. 17, the heat exchanger 10 according to the modification E is arranged so that the first positions L1a and L1b of the adjacent heat transfer units 30a and 30b do not overlap when viewed from the first direction D1. has been done. In other words, the first bulging portions 31pa and 30pb are arranged in a staggered manner in the air passage between the adjacent heat transfer units 30a and 30b. Therefore, compared to the configuration in which the bulging portions are close to each other as shown in FIG. 7, the cross-sectional area of the air passage between the adjacent heat transfer units 31a and 31b can be increased. Therefore, when the heat exchanger 10 is used as an evaporator in a low temperature environment (for example, 7 degrees Celsius or lower), air passage blockage due to frost formation can be further suppressed.

Furthermore, the heat transfer unit 30 may have a second bulge portion that bulges out smaller than the first bulge portion 31p instead of the first plane portion 31q. In this case, the same argument as above holds true.

(5-6) Modification example F
Moreover, the heat transfer unit group 15 according to this embodiment may have a form as shown in FIGS. 18 and 19. Note that FIG. 19 is a partially enlarged view of FIG. 18 (corresponding to the dotted line portion in FIG. 18).

In the example shown in FIGS. 18 and 19, the heat transfer unit 30 (including 30a, 30b, and 30c) bulges out at the first position L1 (including L1a, L1b, and L1c) in the second direction D2, and the heat transfer channel portion The first bulging portion 31p (including 31pa, 31pb, and 31pc) forming the first bulging portion 31 and the first flat portion 31q formed at the first position L1 in the opposite direction to the direction in which the first bulging portion 31p is formed. (31qa, 31qb, 31qc), which is opposite to the direction in which the first bulging portion 31p is formed, bulges at the second position L2 (including L2a, L2b, and L2c) in the second direction D2 and causes a heat transfer flow. A third bulging portion 31r (including 31ra, 31rb, and 31rc) forming the path portion 31 and a second plane formed at the second position L2 in the opposite direction to the direction in which the third bulging portion 31r is formed. 31s (including 31sa, 31sb, and 31sc). Here, the first bulging portion 31p and the third bulging portion 31r have the same shape. Further, the first bulging portion 31p and the third bulging portion 31r are adjacent to each other in the second direction D2.

Moreover, at least one heat transfer unit 30a is adjacent to the heat transfer unit 30b on one side, and the surface on which the first bulging portion 31pa is formed and the first plane portion 31qb of the adjacent heat transfer unit 30b are The formed surfaces are arranged in opposing directions. Moreover, the heat transfer unit 30a is different from the other adjacent heat transfer unit 30c on the other side by the surface on which the third bulging portion 31ra is formed and the second plane portion of the other adjacent heat transfer unit 30c. The surface on which the 30sc is formed is arranged in a direction facing the surface.

Moreover, the first positions L1a, L1b (or L1a, L1c) of the adjacent heat transfer units 30a, 30b (or 30a, 30c) are arranged so as to overlap when viewed from the first direction D1. Further, the second positions L2a and L2b (or L2a and L2c) are also arranged so as to overlap when viewed from the first direction D1. As a supplement, the "first position L1" and "second position L2" are defined for each heat transfer unit, but here they are set to the same position in each heat transfer unit 30a, 30b, 30c. .

In short, in the heat exchanger 10 according to the modification F, the first bulging parts 31pa, 31pb, etc. are formed in opposite directions between the adjacent heat transfer units 30a, 30b without facing each other. Therefore, compared to a configuration in which the first bulging portions 31pa, 31pb, etc. face each other, the occurrence of contractile flow can be suppressed. As a result, an increase in ventilation resistance can be suppressed, and optimal heat exchange performance can be achieved. Further, with the heat exchanger 10 having the above configuration, when used as an evaporator (for example, at temperatures below 7 degrees Celsius), substantially the same bulges as shown in FIG. 7 are formed on both sides of the heat transfer unit. Local frost formation can be suppressed compared to a heat exchanger.

In addition, the heat transfer unit 30 has a second bulging part that bulges out smaller than the first bulging part 31p instead of the first flat part 31q, and a third bulging part 31r instead of the second flat part 31s. It may have a fourth bulge that bulges smaller. In this case, the same argument as above holds true.

(5-7) Modification example G
Moreover, as shown in FIG. 20, the heat exchanger 10 according to the present embodiment has another heat transfer auxiliary part 32 at the end of the heat transfer unit 30 in the second direction D2 when viewed from the first direction D1. A longer heat transfer assisting portion 32g (first heat transfer assisting portion) may be formed. In such a heat exchanger 10, since the distance between the windwardmost heat transfer channel section 31g and the adjacent heat transfer auxiliary section 32g is long, the heat transfer channel section 32g is connected from the windwardmost heat transfer channel section 31g to the heat transfer auxiliary section 32g. The amount of heat transferred to can be reduced. Thereby, the heat flux distribution on the surface of the heat transfer unit 30 can be made uniform. As a result, when the heat exchanger 10 is used as an evaporator in a low temperature environment (for example, 7 degrees Celsius or less), local formation of frost at the entrance of the air path can be suppressed or avoided. .

Furthermore, as shown in FIG. 21, in the heat exchanger 10 according to the present embodiment, the lengths of the heat transfer auxiliary parts 32g in the second direction D2 are made different in the adjacent heat transfer units 30, so that the end portions are They may be arranged in a staggered manner. In such a heat exchanger, a portion with a large cross-sectional area is formed at the entrance of the air passage. Therefore, when the heat exchanger 10 is used as an evaporator in a low temperature environment (for example, 7 degrees Celsius or lower), frost formation at the entrance of the air path can be suppressed or avoided.

(5-8) Modification H
Further, in the heat exchanger 10 according to the present embodiment, as shown in FIG. 22, the heat transfer unit 30 may be processed not only into a linear shape but also into a wave shape when viewed from the first direction D1. When the heat transfer unit 30 is linear, air path resistance can be suppressed. On the other hand, when the heat transfer unit 30 has a corrugated shape, the amount of heat exchanged between the air flow and the refrigerant can be increased. In short, it is possible to provide a heat exchanger with optimal heat exchange performance depending on the usage environment.

(5-9) Modification I
The heat exchanger 10 according to the present embodiment can be applied to a vessel type heat exchanger (small diameter multi-tube heat exchanger) in which heat exchanger tubes and fins are arranged in one direction, but is not limited to this. isn't it. For example, application to a microchannel heat exchanger (flat multi-hole tube heat exchanger) is also possible.

<Other embodiments>
Although the embodiments have been described above, it will be understood that various changes in form and details can be made without departing from the spirit and scope of the claims.

That is, the present disclosure is not limited to the above embodiments as they are. In the implementation stage, the present disclosure can be embodied by modifying the constituent elements without departing from the gist thereof. Moreover, various disclosures can be made in the present disclosure by appropriately combining the plurality of constituent elements disclosed in each of the above embodiments. For example, some components may be deleted from all the components shown in the embodiments. Furthermore, components may be appropriately combined in different embodiments.

10 Heat exchanger 21 First header (upper header)
21p Partition member 22 Second header (lower header)
22p Partition member 22ps Partition member 25 Pressure reduction mechanism 30 Heat transfer unit 30a Heat transfer unit (first heat transfer unit)
30b heat transfer unit (adjacent heat transfer unit on one side)
30c heat transfer unit (adjacent heat transfer unit on the other side)
31 Heat transfer channel section 31p First bulge section 31q First plane section 31r Third bulge section 31s Second plane section 31L Downwind heat transfer channel section 31U Windward heat transfer channel section 32 Heat transfer auxiliary section 32g Second direction end Heat transfer auxiliary part (first heat transfer auxiliary part)
D1 First direction D2 Second direction D3 Third direction I Insulating material L1 First position L2 Second position WL Downwind area WU Windward area

Japanese Patent Application Publication No. 2006-90636

Claims (8)

A plurality of heat transfer flow path sections (31) and a plurality of heat transfer auxiliary sections (32) extending in a first direction (D1) are formed in line in a second direction (D2) orthogonal to the first direction. a heat transfer unit (30) ;
an upper header (21) and a lower header (22) connected to the heat transfer unit from above and below along the first direction and forming part of the refrigerant flow path;
Equipped with
A heat exchanger (10) in which a plurality of the heat transfer units are arranged in a third direction (D3) different from both the first direction and the second direction,
Each of the plurality of heat transfer units is made of a single metal member,
The plurality of heat transfer flow path portions each have an end portion (31e) protruding from the plurality of heat transfer auxiliary portions, and the end portion is inserted into the upper header or the lower header, and the end portion (31e) is inserted into the upper header or the lower header. The heat auxiliary part is not inserted inside the upper header or the lower header,
The heat transfer unit is divided into a windward region (WU) and a leeward region (WL) along the second direction,
When used as an evaporator, the refrigerant is caused to flow into the heat transfer channel section (31U) arranged in the upwind region, and then the refrigerant is caused to flow out into the heat transfer channel section (31L) arranged in the leeward region. ,
The plurality of heat transfer flow path sections (31) belonging to each heat transfer unit (30) include a windward heat transfer flow path section (31U) disposed in the windward region (WU) and a windward heat transfer flow path section (31U) disposed in the windward region (WU), ) a leeward heat transfer flow path section (31L) disposed in
Heat exchanger. The number of heat transfer flow path sections arranged in the leeward region is greater than the number of heat transfer flow path sections arranged in the windward region,
The heat exchanger according to claim 1. further comprising a pressure reduction mechanism (25) that reduces the pressure of the refrigerant,
causing a refrigerant to flow from a heat transfer channel section disposed in the windward region to a heat transfer channel section disposed in the leeward region via the pressure reduction mechanism;
The heat exchanger according to claim 1 or 2. The windward region and the leeward region are formed by partition members (21p, 22p) arranged inside the upper header and/or the lower header,
A heat exchanger according to any one of claims 1 to 3 . Each heat transfer unit has at least eight or more heat transfer flow path sections, and at least two or more heat transfer flow path sections are arranged in the windward region.
A heat exchanger according to any one of claims 1 to 4 . When viewed in the first direction, a heat insulating material (I) is applied to an end of the heat transfer unit in the second direction;
A heat exchanger according to any one of claims 1 to 5 . A first heat transfer auxiliary part (32g), which is one of the heat transfer auxiliary parts, is formed in the heat transfer unit at an end in the second direction when viewed in the first direction,
the first heat transfer auxiliary part has a closed shape;
The heat exchanger according to claim 6 . An air conditioner equipped with the heat exchanger according to any one of claims 1 to 7 .

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