JP7100242B2 - Heat exchanger - Google Patents

Description

Regarding heat exchangers.

Some heat exchangers used in air conditioners and the like have a small-diameter heat transfer tube unit formed by pasting heat transfer fin plates (for example, Patent Document 1 (Japanese Patent Laid-Open No. 2006-90636)). Gazette) etc.).

When the heat exchanger is used as an evaporator in a low temperature environment, concentrated frost formation may occur in a part due to the internal heat flux distribution. Then, the air passage is blocked at the place where the frost formation is concentrated, and the performance of the heat exchanger may be deteriorated.

The heat exchanger of the first aspect has a heat transfer unit formed by arranging a heat transfer flow path portion extending in the first direction and a heat transfer assisting portion in a second direction inclined or orthogonal to the first direction. A plurality of heat transfer units are arranged in a third direction different from both the first direction and the second direction.

Further, in the heat exchanger of the first aspect, the heat transfer unit bulges at the first position in the second direction to form a heat transfer flow path portion, and a first bulging portion is formed. The direction opposite to the direction in which the second bulging portion that bulges smaller than the first flat surface portion or the first bulging portion formed at the first position and the direction in which the first bulging portion is formed are opposite. Then, the third bulging portion that bulges at the second position in the second direction to form the heat transfer flow path portion and the third bulging portion formed at the second position in the direction opposite to the direction in which the third bulging portion is formed. It has two flat surfaces (31s, 31sa, 31sb, 31sc) or a fourth bulging portion that bulges smaller than the third bulging portion.

Here, the at least one heat transfer unit has a surface on which the first bulge is formed and the first plane portion or the second bulge of the adjacent heat transfer unit with the adjacent heat transfer unit on one side. The portions are arranged so as to face the surface on which the portions are formed. Further, the heat transfer unit has a surface on which a third bulge is formed and a second plane portion or a fourth bulge of the other heat transfer unit, which is adjacent to the other heat transfer unit on the other side. Is arranged so as to face the surface on which the surface is formed. With such a configuration, it is possible to realize the optimum heat exchange performance.

The heat exchanger of the second aspect is the heat exchanger of the first aspect, and the first bulging portion and the third bulging portion have the same shape. With such a configuration, fluctuations in the heat flux distribution in the air passage can be suppressed.

The heat exchanger of the third aspect is the heat exchanger of the first aspect or the second aspect, and is arranged so that the first positions in the adjacent heat transfer units overlap each other in the first direction view. With such a configuration, fluctuations in the heat flux distribution in the air passage can be suppressed.

The heat exchanger according to the fourth aspect is the heat exchanger from the first aspect to the third aspect, and the first bulging portion and the third bulging portion are adjacent to each other in the second direction. With such a configuration, it is possible to suppress the occurrence of contraction due to the bulging portion.

The heat exchanger of the fifth aspect is the heat exchanger of the first aspect to the fourth aspect, and is connected to the heat transfer unit from above and below along the first direction to form a part of the flow path of the refrigerant. 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 air conditioner of the sixth aspect is equipped with the heat exchanger of the first aspect to the fifth aspect.

It is a schematic diagram which shows the concept of the heat exchanger 10 which concerns on one Embodiment. It is a schematic diagram which shows the structure of the heat exchanger 10 which concerns on the same embodiment. It is a figure which shows the cross-sectional shape of the 1st header 21 which concerns on the same embodiment. It is a figure which shows the cross-sectional shape of the 2nd header 22 which concerns on the same embodiment. It is a schematic diagram which shows the structure of the heat transfer unit 30 which concerns on the same embodiment. It is a schematic diagram for demonstrating the structure of the heat transfer unit 30 which concerns on the same embodiment. It is a schematic diagram for demonstrating the structure of the heat transfer unit group 15 which concerns on the same embodiment. It is a schematic diagram which shows the cross-sectional shape of the heat exchanger 10 which concerns on the same embodiment. It is a schematic diagram for demonstrating the structure of the heat transfer unit group 15 which concerns on the same embodiment (partially enlarged view of FIG. 7). It is a figure for demonstrating the refrigerant flow path of the heat exchanger 10 which concerns on the same embodiment. It is a schematic diagram which shows the structure of the heat transfer unit 15X for comparison. It is a schematic diagram for demonstrating the structure of the heat transfer unit group 15 which concerns on modification C. It is a schematic diagram for demonstrating the structure of the heat transfer unit group 15 which concerns on modification C. It is a schematic diagram for demonstrating the structure of the heat transfer unit group 15 which concerns on modification D. It is a schematic diagram for demonstrating the structure of the heat transfer unit group 15 which concerns on modification E. It is a schematic diagram for demonstrating the structure of the heat transfer unit group 15 which concerns on modification E. It is a figure for demonstrating the refrigerant flow path of the heat transfer unit group 15 which concerns on modification F.

(1) Outline of heat exchanger The heat exchanger 10 exchanges heat between the fluid flowing inside and the air flowing outside. Specifically, as shown in the concept of FIG. 1, the heat exchanger 10 is provided with a first pipe 41 and a second pipe 42 for the refrigerant to flow in and out. Further, in the vicinity of the heat exchanger 10, a fan 6 for sending wind to the heat exchanger 10 is arranged. The fan 6 generates an air flow toward the heat exchanger 10, and when the air flow passes through the heat exchanger 10, heat exchange is performed between the heat exchanger 10 and the air. The heat exchanger 10 functions as both an evaporator that takes heat from the air and a condenser (radiator) that releases heat to the air, and can be mounted on an air conditioner or the like.

(2) Details of heat exchanger (2-1) Overall configuration As shown in FIG. 2, the heat exchanger 10 has 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 so that the direction of the air flow generated by the fan 6 passes between the heat transfer units 30. Details of 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 so that a refrigerant in a gas / liquid / gas-liquid two-phase state can flow inside. .. Then, the first header 21 is connected to the first pipe 41 and the heat transfer unit 30 above the heat transfer unit 30. Further, 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 is formed in the connecting surface 21S into which the end portion 31e of the heat transfer flow path portion 31, which will be described later, is inserted. Note that FIG. 3 shows the cross-sectional state of the first header 21 when viewed from the third direction D3. The definition of the third direction D3 will be described later.

As shown in FIG. 4, the second header 22 is composed of a hollow member like the first header 21, and is configured so that a refrigerant in a gas / liquid / gas-liquid two-phase state can flow inside. There is. Then, the second header 22 is connected to the second pipe 42 and the heat transfer unit 30 below the heat transfer unit 30. Further, 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 is formed in the connecting surface 22S into which the end portion 31e of the heat transfer flow path portion 31, which will be described later, is inserted. Note that FIG. 4 shows the cross-sectional state 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, in the heat transfer unit 30, a plurality of heat transfer flow path portions 31 and a plurality of heat transfer assisting portions 32 extending in the “first direction D1” are inclined or orthogonal to the first direction D1. It is formed side by side in the second direction D2. Here, the heat transfer flow path portion 31 has a substantially semi-cylindrical shape, and the heat transfer auxiliary portion 32 has a substantially flat plate shape. Further, as shown in FIG. 6, the heat transfer flow path portion 31 is formed so as to be lined up in the second direction D2 at a predetermined pitch PP. By arranging a plurality of such heat transfer units 30 in the "third direction D3" which is different from both the first direction D1 and the second direction D2, the heat transfer unit group 15 as shown in FIG. 7 is formed. 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, the first direction D1, the second direction D2, and the third direction D3 are assumed to be orthogonal to each other. However, even if these directions D1 to D3 are not completely orthogonal to each other, it is possible to realize the heat exchanger 10 according to the present embodiment as long as they are inclined to each other.

The heat transfer unit 30 is connected to the first header 21 and the second header 22 at the connection surfaces 21S and 22S of the first header 21 and the second header 22. Specifically, as shown in FIG. 5, the end portion of the heat transfer unit 30 in the first direction has the end portion 31e of the heat transfer flow path portion 31 protruding from the end portion 32e of the heat transfer assist portion 32. The end portion 31e of the heat transfer flow path portion 31 is inserted into the connecting holes provided in the connection 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 portion (see FIG. 8).

The heat transfer flow path portion 31 enables the movement of the refrigerant between the first header 21 and the second header 22. Specifically, a substantially cylindrical passage is formed inside the heat transfer passage portion 31, and the refrigerant moves in this passage. The heat transfer flow path portion 31 according to the present embodiment is formed linearly along the first direction D1.

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

(2-3-2)
A specific embodiment of the heat transfer unit 30 according to the present embodiment will be described with reference to FIG. Note that FIG. 9 is a partially enlarged view of FIG. 7 (corresponding to the dotted line portion of FIG. 7).

The heat transfer unit 30 (including 30a, 30b, 30c) according to the present embodiment bulges at the first position L1 (including L1a, L1b, L1c) in the second direction D2 to form the heat transfer flow path portion 31. The first flat surface portion 31q (31qa, 31qb) formed at the first position L1 in the direction opposite to the direction in which the first bulging portion 31p (including 31pa, 31pb, 31pc) and the first bulging portion 31p are formed. , 31qc) and the direction opposite to the direction in which the first bulging portion 31p is formed, bulging at the second position L2 (including L2a, L2b, L2c) in the second direction D2 to form the heat transfer channel portion 31. The third bulging portion 31r (including 31ra, 31rb, 31rc) to be formed and the second plane portion 31s (31sa) formed at the second position L2 in the direction opposite to the direction in which the third bulging portion 31r is formed. , 31sb, 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.

Further, the heat transfer unit 30b adjacent to at least one heat transfer unit 30a on one side includes a surface on which the first bulging portion 31pa is formed and a first flat surface portion 31qb of the adjacent heat transfer unit 30b. It is arranged so that the surface to be formed faces the opposite direction. Further, the heat transfer unit 30a has a surface on which the third bulging portion 31ra is formed and a second plane portion of the other adjacent heat transfer unit 30c, which is adjacent to the other heat transfer unit 30c on the other side. It is arranged so as to face the surface on which 31 sc is formed.

Further, the first positions L1a, L1b (or L1a, L1c) in the adjacent heat transfer units 30a, 30b (or 30a, 30c) are arranged so as to overlap each other when viewed from the first direction D1. Further, the second positions L2a, L2b (or L2a, L2c) are also arranged so as to overlap each other when viewed from the first direction D1. Supplementally, "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. ..

(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, the liquid phase refrigerant F flows into the heat exchanger 10 from the second pipe 42. Subsequently, the refrigerant F flows from the second pipe 42 into the second header 22. Then, the refrigerant F flows from the lower side to the upper side via the heat transfer flow path portion 31 connected to the second header 22. The refrigerant F exchanges heat with the air flow W while flowing through the heat transfer flow path portion 31. As a result, the refrigerant F evaporates and changes to a gas phase. Then, the gas phase refrigerant F flows out from the first pipe 41.

When the heat exchanger 10 is used as a condenser, the refrigerant F flows in the opposite direction to that of the 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) Manufacturing Method of Heat Exchanger 10 The heat transfer unit 30 is manufactured from a metal material such as aluminum or an aluminum alloy. Specifically, first, extrusion molding of a metal material is performed using a mold corresponding to the cross-sectional shape of FIG. 5, and a heat transfer flow path portion 31 and a heat transfer assist portion 32 are integrally formed. Subsequently, a part of the heat transfer assisting portion 32 is cut off to provide a notch 33. For example, the notch 33 is formed by cutting out a plurality of heat transfer assisting portions 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 for inserting the end portion 31e of the heat transfer flow path portion 31. The connecting hole is, for example, a circular through hole formed by a drill.

In assembling the heat exchanger 10, the end 31e of the heat transfer flow path portion 31 of the heat transfer unit 30 is inserted into the connecting holes of the first header 21 and the second header 22. As a result, the end portion 32e of the heat transfer assisting 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 point, the heat transfer unit 30, the first header 21, and the second header 22 are brazed and fixed.

(4) Features (4-1)
As described above, in the heat exchanger 10 according to the present embodiment, the heat transfer flow path portion 31 extending in the first direction D1 and the heat transfer assisting portion 32 are inclined or orthogonal to the first direction D1 in the second direction D2. It has a heat transfer unit 30 formed side by side. Here, a plurality of heat transfer units 30 are arranged in the third direction D3, which is different from both the first direction D1 and the second direction D2, to form the heat transfer unit group 15. In this embodiment, for convenience of explanation, the directions D1 to D3 are orthogonal to each other.

Further, in the heat exchanger 10 according to the present embodiment, the heat transfer unit 30 (including 30a, 30b, 30c) bulges at the first position L1 (including L1a, L1b, L1c) in the second direction D2. The first bulging portion 31p (including 31pa, 31pb, 31pc) forming the heat transfer flow path portion 31 is formed at the first position L1 in the direction opposite to the direction in which the first bulging portion 31p is formed. At the second position L2 (including L2a, L2b, L2c) in the second direction D2, which is opposite to the direction in which the first flat surface portion 31q (31qa, 31qb, 31qc) and the first bulging portion 31p are formed. The third bulging portion 31r (including 31ra, 31rb, 31rc) that bulges to form the heat transfer flow path portion 31 and the third bulging portion 31r are formed at the second position L2 in the direction opposite to the direction in which the third bulging portion 31r is formed. It has a second plane portion 31s (including 31sa, 31sb, 31sc) to be formed.

Further, the heat transfer unit 30b adjacent to at least one heat transfer unit 30a on one side is a surface on which the first bulging portion 31pa is formed and a first flat surface portion 31qb of the adjacent heat transfer unit 30b. It is arranged so that the surface to be formed faces the opposite direction. Further, the heat transfer unit 30a has a surface on which the third bulging portion 31ra is formed and a second plane portion 31sc of the other heat transfer unit 30b with the other heat transfer unit 30c adjacent to each other on the other side. It is arranged so that the surface to be formed faces the opposite direction.

In short, in the heat exchanger 10 according to the present embodiment, the first bulging portions 31pa, 31pb (or 31pa, 31pc) and the like do not face each other between the adjacent heat transfer units 30a, 30b (or 30a, 30c). In addition, it is formed in the opposite direction. Therefore, the occurrence of contraction can be suppressed as compared with the configuration in which the first bulging portions 31pa, 31pb and the like face each other. As a result, it is possible to suppress an increase in ventilation resistance and realize optimum heat exchange performance. Further, in the case of the heat exchanger 10 having the above configuration, when used as an evaporator in a low temperature environment (for example, 7 degrees Celsius or less), substantially the same bulging portion as shown in FIG. 11 is the heat transfer unit 15X. Local frost formation can be suppressed as compared with heat exchangers formed on both sides.

(4-2)
Further, in the heat exchanger 10 according to the present embodiment, the first bulging portion 31p and the third bulging portion 31r have the same shape. With such a configuration, fluctuations in the heat flux distribution in the air passage 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 less), local generation of frost formation can be suppressed.

However, the heat exchanger 10 according to the present embodiment is not limited to the above configuration, and the first bulging portion 31p and the third bulging portion 31r may have different shapes.

(4-3)
Further, in the heat exchanger 30 according to the present embodiment, when the first positions L1a, L1b (or L1a, L1c) of the adjacent heat transfer units 30a, 30b (or 30a, 30c) are viewed from the first direction D1. It is arranged so as to overlap with. With such a configuration, fluctuations in the heat flux distribution in the air passage can be suppressed.

Further, in the heat exchanger 30 according to the present embodiment, in addition to the configuration in which the first positions L1a, L1b (or L1a, L1c) overlap when viewed from the first direction D1, the second positions L2a, L2b (or) L2a, L2c) are also arranged so as to overlap each other. The heat exchanger 10 having such a configuration can be realized by stacking heat transfer units 30a, 30b, and 30c having the same shape (see FIG. 7). Therefore, the heat exchanger 10 can be easily manufactured. As a result, with the above configuration, it is possible to mass-produce the heat exchanger 10 capable of suppressing fluctuations in the heat flux distribution.

The heat exchanger 10 according to this embodiment is not limited to the above configuration. In other words, in the heat exchanger 10 according to the present embodiment, the first positions L1a, L1b (or L1a, L1c) of the adjacent heat transfer units 30a, 30b (or 30a, 30c) are viewed from the first direction D1. It does not exclude shapes that sometimes do not overlap.

(4-4)
Further, in the heat exchanger 30 according to the present embodiment, the first bulging portion 31p and the third bulging portion 31r are adjacent to each other in the second direction D2. In other words, the first bulging portion 31p and the third bulging portion 31r that bulge in opposite directions are formed adjacent to each other. With such a configuration, it is possible to suppress the occurrence of contraction due to the bulging portion. Therefore, it is possible to suppress an increase in ventilation resistance. 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 generation of frost formation can be suppressed.

(4-5)
Further, the heat exchanger 10 according to the present embodiment is connected to the heat transfer unit 30 from above and below along the first direction D1 to form a part of the refrigerant flow path, the first header 21 (upper header) and the second header. A header 22 (lower header) is further provided. With such a configuration, the longitudinal direction of the heat transfer unit 30 can be directed in the vertical direction, and the adhering water (condensation water, etc.) can be easily discharged. In addition, it is possible to improve assemblability and workability.

However, the heat exchanger 10 according to the present embodiment does not exclude the configuration in which the first header 21 and the second header 22 are provided in the left-right direction instead of the up-down direction.

(4-6)
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. Further, a plurality of notches 33 can be formed at one time by punching. Therefore, it is possible to provide the heat exchanger 10 having high assembleability and workability.

(5) Modification example (5-1) Modification example A
The heat exchanger 10 according to the present embodiment may have a heat transfer unit 30 having a second bulging portion that bulges smaller than the first bulging portion 31p instead of the first flat surface portion 31q. Further, the heat transfer unit 30 may have a fourth bulging portion that bulges smaller than the third bulging portion 31r instead of the second flat surface portion 31s. Even in this case, the same argument as above holds.

When the heat transfer unit 30 has a second bulging portion and a fourth bulging portion, the second bulging portion and the fourth bulging portion may have the same shape.

(5-2) Modification B
Further, the heat transfer flow path portion 31 according to the present embodiment is not limited to the above-mentioned one, and may be another form. 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 flat shape, an upper half shape of an airfoil, and / or a lower half shape of an airfoil. It may be one or any combination. In short, the heat exchanger 10 can adopt a shape that optimizes the heat exchange performance.

(5-3) Modification C
Further, in the heat exchanger 10 according to the present embodiment, the heat transfer unit 30 has a heat transfer assisting portion 32g (first heat transfer assisting portion) at the end of the second direction D2 when viewed from the first direction D1. It may be a thing. Here, the length of the heat transfer assisting portion 32 g in the second direction D2 is formed to be longer than the predetermined pitch PP in the second direction D2. In other words, as shown in FIG. 12, the heat exchanger 10 transfers heat to the end of the second direction D2 in the heat transfer unit 30 longer than the other heat transfer assisting parts 32 when viewed from the first direction D1. A heat assisting portion 32g (first heat transfer assisting portion) may be formed. In such a heat exchanger 10, since the distance between the heat transfer channel portion 31 g on the uppermost wind side and the adjacent heat transfer auxiliary portion 32 g is long, the heat transfer auxiliary portion 32 g from the heat transfer channel portion 31 g on the uppermost wind side. The amount of heat transfer to can be reduced. As a result, 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 frost formation at the inlet of the air passage can be suppressed or avoided. ..

Further, as shown in FIG. 13, the heat exchanger 10 according to the present embodiment has the end portions of the adjacent heat transfer units 30 having different lengths of the heat transfer assisting portions 32 g in the second direction D2. It may be arranged in a staggered pattern. In such a heat exchanger, a portion having a wide cross-sectional area is formed at the inlet portion 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 less), frost formation at the inlet of the air passage can be suppressed or avoided.

(5-4) Modification D
Further, as shown in FIG. 14, the heat exchanger 10 according to the present embodiment may have the heat transfer unit 30 processed into a wavy shape as well as a linear shape when viewed from the first direction D1. When the heat transfer unit 30 is linear, the air passage resistance can be suppressed. On the other hand, when the heat transfer unit 30 has a wave shape, the amount of heat exchange between the wind and the refrigerant can be increased. In short, it is possible to provide a heat exchanger having optimum heat exchange performance according to the usage environment.

(5-5) Modification E
Further, in the heat exchanger 10 according to the present embodiment, even if the heat insulating material I is applied to the wind-upper end of the second direction D2 of the heat transfer unit 30 when viewed from the first direction D1. Good (see Figures 15 and 16). As a result, it is possible to suppress a decrease in temperature at the end portion. As a result, when the heat exchanger 10 is used as an evaporator in a low temperature environment (eg, 7 degrees Celsius or less), frost formation can be suppressed and air passage blockage can be avoided or delayed.

In the examples shown in FIGS. 15 and 16, the end portion of the heat transfer unit 30 is the heat transfer assisting portion 32g. Further, the heat transfer assisting portion 32g (first heat transfer assisting portion) on the uppermost windward side has a closed shape. Here, the "closed shape" is a shape without holes, cuts, etc., and means a flat shape. This makes it possible to further improve the drainage property during the defrosting operation.

Supplementally, if a hole, a notch, or the like is formed in the heat transfer assisting portion 32 g, the water generated by melting the frost may be retained in the hole or the notch. Then, in that case, the water-retained portion may be the starting point of the next frost formation. On the other hand, in the heat exchanger 10 according to the modified example E, since the heat transfer assisting portion 32g has a shape without holes or cuts, it is possible to suppress frost formation that occurs after the defrosting operation.

(5-6) Modification F
Further, in the heat exchanger 10 according to the present embodiment, the refrigerant flow path may be folded back at least once in the second direction D2 where the air flow W is generated. For example, the refrigerant flow path as shown in FIG. 17 may be adopted. Here, the inside of the second header 22 is divided into an upwind second header 22U on the leeward side and a leeward second header 22L on the leeward side, and the second pipe 42 is connected to the upwind second header 22U. The first pipe 41 is connected to the leeward second header 22L.

In such a configuration, the refrigerant temperature in the windward heat transfer flow path portion 31U (hereinafter, also referred to as windward heat transfer flow path portion 31U) becomes high due to the pressure loss. Therefore, when the heat exchanger 10 is used as an evaporator, the amount of heat exchange in the upwind heat transfer flow path portion 31U is suppressed. As a result, it is possible to suppress fluctuations in the heat flux depending on the position in the heat transfer unit group 15. 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 frost formation can be avoided, and heat exchange with excellent heat exchange performance can be avoided. Can provide vessels.

Further, in such a configuration, since all of the refrigerant F flowing in from the second pipe 42 is once flowed to the heat transfer flow path portion on the windward side, the refrigerant may be completely evaporated in the heat transfer flow path portion 31U on the windward side. It can be avoided. As a result, the heat exchange performance of the heat exchanger 10 can be optimized.

(5-7) Modification G
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 transfer tubes and fins are arranged in one direction, but is limited to this. is not. For example, it can be applied to a microchannel type heat exchanger (flat multi-hole tube heat exchanger).

<Other embodiments>
Although the embodiments have been described above, it will be understood that various modifications of the embodiments and details are possible without departing from the spirit and scope of the claims.

That is, the present disclosure is not limited to each of the above embodiments as they are. In the present disclosure, the components can be modified and embodied within the range that does not deviate from the gist at the implementation stage. Further, in the present disclosure, various disclosures can be formed by an appropriate combination of the plurality of components disclosed in each of the above embodiments. For example, some components may be removed from all the components shown in the embodiments. Further, the components may be appropriately combined in different embodiments.

10 Heat exchanger 21 1st header (upper header)
22 Second header (lower header)
30 Heat transfer unit 30a Heat transfer unit (one 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 31p 1st bulging 31q 1st flat surface 31r 3rd bulging 31s 2nd flat 32 Heat transfer assisting part 32g Heat transfer assisting part at the end in the 2nd direction (1st heat transfer assisting part) )
D1 1st direction D2 2nd direction D3 3rd direction I Insulation material L1 1st position L2 2nd position

Japanese Unexamined Patent Publication No. 2006-90636

Claims (7)

A plurality of heat transfer flow path portions (31) and heat transfer assisting portions (32) extending in the first direction (D1) are formed side by side in a second direction (D2) inclined or orthogonal to the first direction. A heat exchanger (10) having heat units (30, 30a, 30b, 30c) and having a plurality of heat transfer units arranged in a third direction (D3) different from both the first direction and the second direction. And,
Each of the plurality of heat transfer units (30) has a plurality of refrigerant channels for guiding the refrigerant.
At least one of the refrigerant flow paths is provided in each of the plurality of heat transfer flow path portions (31).
The heat transfer assisting portion (32) is not provided with the refrigerant flow path, and the heat transfer assisting portion (32) is not provided with the refrigerant flow path.
The heat transfer assisting portion (32) has a third-direction dimension and the second-direction dimension larger than the third-direction dimension.
Each of the plurality of heat transfer units has a first surface and a second surface located opposite to the first surface.
The first surface is provided with a first bulging portion (31p, 31pa, 31pb, 31pc) that bulges at the first position (L1) in the second direction to form the heat transfer flow path portion.
The second surface is provided with a first flat surface portion (31q, 31qa, 31qb, 31qc) formed at the first position or a second bulging portion that bulges smaller than the first bulging portion.
The second surface is further provided with a third bulging portion (31r, 31ra, 31rb, 31rc) that bulges at the second position (L2) in the second direction to form the heat transfer flow path portion.
The first surface is further provided with a second flat surface portion (31s, 31sa, 31sb, 31sc) formed at the second position or a fourth bulging portion that bulges smaller than the third bulging portion.
The plurality of heat transfer units include a first heat transfer unit (30a), a second heat transfer unit (30b) adjacent to the first heat transfer unit, and a third heat transfer unit adjacent to the first heat transfer unit. Has a unit (30c) and
The first surface of the first heat transfer unit (30a) and the second surface of the second heat transfer unit (30b) face each other.
The second surface of the first heat transfer unit (30a) and the first surface of the third heat transfer unit (30c) face each other.
Heat exchanger. Each of the plurality of first bulging portions is provided with one said refrigerant flow path.
Each of the plurality of the third bulging portions is provided with one said refrigerant flow path.
The heat exchanger according to claim 1 . The first bulging portion and the third bulging portion have the same shape.
The heat exchanger according to claim 1 or 2 . The first positions of adjacent heat transfer units are arranged so as to overlap each other in the first direction view.
The heat exchanger according to any one of claims 1 to 3 . The first bulging portion and the third bulging portion are adjacent to each other in the second direction.
The heat exchanger according to any one of claims 1 to 4 . The heat transfer unit is further provided with an upper header (21) and a lower header (22) that are connected from above and below along the first direction and form a part of the flow path of the refrigerant.
The heat exchanger according to any one of claims 1 to 5 . An air conditioner equipped with the heat exchanger according to any one of claims 1 to 6 .

Images