heat exchanger

Abstract

Heat exchanger (10) with juxtaposed tubes (21) and a container (31) connected to ends (21a) of the tubes (21), wherein the heat exchanger (10) carries out a heat exchange between a first fluid flowing inside the tubes (21) and a second fluid flowing outside the tubes (21), the heat exchanger (10) comprising: a closure member (50) disposed within the container (31) and partially closing an opening provided at one end (21a) of a predetermined tube (21A) which is at least one of the tubes (21), wherein the predetermined tube (21A) has a projection (215) formed at one end (21a) of the predetermined tube (21A), and the closure member (50) has an avoidance structure (51, 54) which avoids an interference between the projection (215) and the closure member (50), characterized in that the tubes (21) have a metal plate (210) which is bent into a tubular shape, the metal plate (210) has a joint (214) at which both ends (212, 213) of the metal plate (210) are joined to a central portion of the metal plate (210), the projection (215) is formed at the joint (214), and the avoidance structure (51, 54) is formed at a position facing the joint (214).

Description

Technical FieldThe present disclosure relates to a heat exchangerPrior ArtConventionally, there is a heat exchanger described in Patent Literature 1 shown below. The heat exchanger described in Patent Literature 1 has a heat exchanger core, an inlet tank, and an outlet tank. The heat exchanger core is formed by stacking tubes through which an internal fluid flows. The one ends of the tubes are inlet ends and the other ends are outlet ends. The inlet tank is joined to the inlet ends of the tubes so that an interior of the inlet tank communicates with the interior of the tubes. The inlet tank distributes the internal fluid to the tubes. The outlet tank is joined to the outlet ends of the tubes so that an interior of the outlet tank communicates with the interior of the tubes. The outlet container therein collects the internal fluid from the tubes. One end of the inlet tank in a pipe stacking direction has an inflow port for allowing the internal fluid to flow into the inlet tank. One end of the outlet tank in the tube stacking direction has an outlet port facing in the same direction as a direction in which the inflow port faces. The outlet port allows the internal fluid to flow out of the outlet container. A closing member is provided at ends of a predetermined number of tubes adjacent to the inflow port in the tube stacking direction. The closure member partially closes openings provided at the ends of the predetermined number of tubes. According to such a configuration, the closure member can reduce flows of the internal fluid flowing into the tubes disposed near the inflow port, while the closure member can increase flows of the internal fluid flowing into tubes disposed away from the inflow port. As a result, it is possible to equalize the flows in the tubes.Patent Literature 2 shows a heat exchanger having the features of the preamble of claim 1. Patent Literature 3 shows another prior art heat exchanger.Prior Art LiteraturePatent LiteraturePatent Literature 1: JP 4 830 918 B2Patent Literature 2: US 2012 0 267 086 A1Patent Literature 3: WO 2020 / 012 921 A1SUMMARY OF THE INVENTIONIn such a heat exchanger as that described in Patent Literature 1, a protrusion may be formed at an end of a pipe. More specifically, the tube is manufactured by bending a metal plate into a tube shape, joining both ends of the metal plate together, and then cutting the metal plate to a predetermined length. When the pipe is manufactured in this manner, a burr can be formed on a cut surface at the time of cutting the pipe product. It has been confirmed by the inventors of the present disclosure that the burr formed at the time of cutting is likely to be formed particularly at the joint of the both ends of the metal plate. The burr or the like formed in this manner may form the protrusion at the end of the pipe.If the protrusion is formed at the end of the pipe, the closing member may be raised by the protrusion of the pipe at the time of placing the closing member described in Patent Literature 1 at the end of the pipe. If the closing member is raised by the projection of the tube, it will become difficult for the closing member to close an opening of the tube. Further, for example, variations in the protruding length of the end of the tube may make it difficult for the closure member to close the end of the tube. When the effect of closing the end of the pipe by the closing member is reduced by these various factors, it becomes difficult to reduce a flow rate of a fluid flowing into the pipe in the vicinity of the inflow port, and as a result, uniformity of distribution of the fluid in the pipes cannot be improved.An object of the present disclosure is to provide a heat exchanger capable of improving uniformity of distribution of fluid in tubes.The aforementioned object is achieved with a heat exchanger having the features of claim 1. Advantageous refinements are set out in the dependent claims.According to an aspect of the present disclosure, a heat exchanger includes tubes arranged side by side and a tank connected to ends of the tubes. The heat exchanger performs heat exchange between a first fluid flowing inside the tubes and a second fluid flowing outside the tubes. The heat exchanger has a closing member that is disposed inside the container and partially closes an opening provided at an end of a predetermined tube that is at least one of the tubes. The predetermined tube has a protrusion formed at the end of the predetermined tube. The shutter member has an avoiding structure that avoids interference between the protrusion and the shutter member.According to this configuration, the avoiding structure formed in the closing member can avoid interference between the protrusion formed at the end of the predetermined tube and the closing member. Therefore, it becomes difficult for the shutter member to be raised by the protrusion. As a result, the end of the predetermined pipe can be closed with higher safety by the closing member, so that the uniformity of distribution of the fluid in the pipes can be improved.Brief Description of the DrawingsFIG. 1 is a front view illustrating a front structure of a heat exchanger of a first embodiment. FIG. 2 is a cross-sectional view illustrating a cross-sectional structure of tubes of the first embodiment. FIG. 3 is a cross-sectional view illustrating a cross-sectional structure of a first container according to the first embodiment in a cross-section perpendicular to a pipe longitudinal direction. FIG. 4 is a perspective view illustrating a cut-out cross-sectional structure of the heat exchanger according to the first embodiment provided with a first tank member of the first tank, cut along the cross section perpendicular to the pipe longitudinal direction. FIG. 5 is a cross-sectional view taken along a line V-V of FIG. 3. FIG. 6 is a perspective view illustrating a cross-sectional structure of a closure member of the first embodiment. FIG. 7 is a cross-sectional view illustrating a cross-sectional structure of a first tank of a heat exchanger according to a reference example in a sectional plane perpendicular to a pipe longitudinal direction. FIG. 8 is a cross-sectional view illustrating a cross-sectional structure of a closure member according to a modification of the first embodiment. FIG. 9 is a cross-sectional view illustrating a cross-sectional structure of a closure member according to a modification of the first embodiment. FIG. 10 is a cross-sectional view illustrating a cross-sectional structure of a first tank of a heat exchanger according to a modification of the first embodiment, taken in a sectional plane perpendicular to an air flow direction. FIG. 11 is a perspective view illustrating a closure member of a second embodiment. FIG. 12 is a perspective view illustrating a closure member of a modification of the second embodiment.DETAILED DESCRIPTIONIn the following, an exemplary embodiment of a heat exchanger is described with reference to the figures. In order to facilitate understanding, identical constituent elements are denoted by identical reference numerals in the drawings, and the duplicated description thereof will be omitted.First EmbodimentFirst, a heat exchanger 10 according to a first embodiment shown in FIG. 1 will be described.The heat exchanger 10 of the present embodiment is used as, for example, a heater core of an air conditioner mounted on a vehicle. The air conditioner is a device that heats or cools an air and blows the air into a vehicle compartment, thereby heating or cooling the vehicle compartment. The heat exchanger 10 is disposed in an air conditioning duct through which air conditioning air flows. Cooling water of an engine of the vehicle circulates inside the heat exchanger 10 in a liquid phase. The heat exchanger 10 heats the air-conditioning air by heat exchange between the cooling water flowing through the heat exchanger 10 and the air-conditioning air flowing through the air-conditioning duct. The air-conditioning air heated at the heat exchanger 10 is blown into the vehicle compartment through the air-conditioning duct, thereby heating the vehicle compartment. In this embodiment, the cooling water flowing inside the heat exchanger 10 corresponds to a fluid. Further, the cooling water corresponds to a first fluid and the air corresponds to a second fluid.As shown in FIG. 1, the heat exchanger 10 has a core 20, tanks 31, 32, and side plates 41, 42.The core 20 performs heat exchange between the cooling water and the air. The core 20 has tubes 21 and fins 22, and the tubes 21 are stacked with each other in a direction indicated by an arrow X in the drawings at predetermined intervals. The fins 22 are arranged in gaps defined between adjacent tubes 21. FIG. 1 shows a part of the louvers 22. The direction indicated by the arrow Y is a direction perpendicular to the direction indicated by the arrow X. A direction indicated by an arrow Z in the drawings is a direction perpendicular to the direction indicated by the arrow X and the direction indicated by the arrow Y.Hereinafter, the direction indicated by the arrow X is referred to as a "pipe stacking direction X". Further, one direction in the pipe stacking direction X is referred to as an "X 1 direction", and the other opposite direction in the pipe stacking direction X is referred to as an "X 2 direction". Further, the direction indicated by the arrow Y is referred to as an "air flow direction Y".The tubes 21 are provided so as to extend in the direction indicated by the arrow Z in the drawings. Hereinafter, the direction indicated by the arrow Z is referred to as a "pipe length direction Z". Further, one direction in the pipe length direction Z is referred to as a "Z 1 direction", and the other opposite direction in the pipe length direction Z is referred to as a "Z 2 direction". As shown in FIG. 2, each pipe 21 of the pipes 21 has an inner passage W 10 through which the cooling water flows. The tube 21 is formed by bending a metal plate 210 into a tube shape.More specifically, in manufacturing the tube 21, first, a central portion of the metal plate 210 having a flat shape is doubly bent to have a folded portion forming a protruding portion 211. Then, both ends 212, 213 of the metal plate 210 are bent inward so that the both ends are in contact with the protruding portion 211. And then, the both ends 212, 213 and the protruding portion 211 are joined by brazing, thereby forming a tube product. The tube 21 is finally formed by cutting the tube product to a predetermined length. In the pipe 21 of the present embodiment, an inner passage W 10 of the pipe 21 is divided into two flow paths W 11, W 12 by a joint 214 at which the both ends of the metal plate 210 and the protruding portion 211 are joined.As shown in FIG. 1, each sipe 22 of the sipes 22 is a so-called corrugated sipe formed by bending a thin and long metal plate into a corrugated shape. Bent portions of the fin 22 are joined to outer walls of adjacent two tubes 21, 21 by brazing. The fin 22 improves heat exchange efficiency between the cooling water and the air by increasing a heat transfer area for air.The containers 31, 32 are each a tubular member extending in the tube stacking direction X. The tanks have a first tank 31 and a second tank 32. as shown in FIGS. 3 and 4, an inner passage W 20 through which the cooling water flows is defined in the first tank 31. As shown in FIG. 5, the first container 31 has a first container member 312 and a second container member 313. Shapes of the first tank member 312 and the second tank member 313 in sectional planes perpendicular to the tube stacking direction X are recessed. The first container 31 is obtained by joining the first container member 312 and the second container member 313. As shown in FIGS. 3 to 5, the first tank 31 is connected to the one ends 21 aof the tubes 21. The one ends 21 aof the tubes 21 are arranged to extend through the second tank member 313 of the first tank 31 to the inner passage W 20 of the first tank 31. As shown in FIG. 1, an inflow port 33 is attached to an end 310 of the first container 31 facing in the X2 direction. The other end 311 of the first container 31 facing in the X 1 direction is closed.Like the first tank 31, the second tank 32 is also a pipe member in which a flow path for the cooling water is formed. The second tank 32 is connected to the other ends 21 bof the tubes 21. An outlet port 34 is attached to an end 320 of the second container 32 facing in the X3 direction. The other end 321 of the second container 32 facing in the X 1 direction is closed.Side plates 41, 42 are respectively disposed at different ends of the core 20 in the tube stacking direction X. The one ends 410, 420 of the side plates 41, 42 in the Z2 direction are connected to the first container 31. As shown in FIG. 3, one end 410 of a side plate 41 is disposed to extend through the second tank member 313 of the first tank 31 to the inner passage W 20 of the first tank 31. Likewise, one end 420 of a side plate 42 is also connected to the first container 31. Further, as shown in FIG. 1, the other ends 411, 421 of the side plates 41, 42 facing in the Z 1 direction are connected to the second container 32. The side plates 41, 42 are provided to reinforce the core 20.As shown in FIGS. 3 to 5, the heat exchanger 10 further includes a closure member 50 accommodated in the first tank 31. The closure member 50 is a member separate from the first container 31, and is disposed inside the first container 31 by being inserted into the first container 31 from the inflow port 33. As shown in FIG. 6, the shutter member 50 is formed in a flat plate shape. As shown in FIG. 3, the closure member 50 is provided at ends 21 aof a predetermined number of the tubes 21 disposed in the vicinity of the inflow port 33. The closing member 50 partially closes openings provided at the ends 21 aof the predetermined number of tubes 21. More specifically, the closing member 50 is provided to close openings of flow paths W 11 at the ends 21 aof the predetermined number of tubes 21. Hereinafter, for convenience, the tubes 21 that are disposed near the inflow port 33 and have flow paths partially closed by the closing member 50 will be referred to as "predetermined tubes 21A". As shown in FIG. 3, an end of the shutter member 50 facing in the X 2 direction has a protrusion 55 extending toward an inside of the inflow port 33. As shown in FIG. 4, a bottom surface of the protrusion 55 facing in the Z 1 direction has an engaging portion 550. The engaging portion 550 is engaged with an end surface of the second container member 313 of the first container 31 facing in the X2 direction. The engagement between the engagement portion 550 and the second container member 313 of the first container 31 restricts displacement of the closure member 50 in the X 1 direction.Next, an exemplary operation of the heat exchanger 10 of the present embodiment will be described.In the heat exchanger 10, liquid-phase cooling water flows into the first tank 31 through the inflow port 33, The cooling water that has flowed into the first tank 31 is distributed to the tubes 21 by flowing into the inner passage W 10 from the one ends 21 aof the tubes 21. The cooling water distributed to the tubes 21 flows toward the second tank 32 through the inner passage W 10 of the tubes 21, and the heat exchanger 10 performs heat exchange between the cooling water flowing through the inner passages W 10 of the tubes 21 and the air flowing outside the tubes 21. As a result, the air is heated by heat of the cooling water transferred to the air. The cooling water having passed through the tubes 21 is collected in the second tank 32 and then discharged from the outlet port 34. As described above, the heat exchanger 10 of the present embodiment has a so-called all-pass type structure (all-pass type structure) in which cooling water from the first tank 31 is distributed to all the tubes 21.On the other hand, in the structure of the heat exchanger 10 in which the cooling water flows into the first tank 31 from the inflow port 33 provided at one end of the first tank 31 as shown in FIG. 3, a length of a flow path of the cooling water increases, and a pressure loss of the cooling water increases as the cooling water flows toward the closed end 311. Therefore, a flow rate of the cooling water flowing into one of the tubes 21 disposed away from the inflow port 33 becomes smaller than a flow rate of the cooling water flowing into another one of the tubes 21 disposed in the vicinity of the inflow port 33. As a result, the flows of the cooling water of the tubes 21 may be unequal. If the flows of the cooling water of the tubes 21 are unequal, a temperature distribution in the air after the heat exchange will not be uniform, which may result in deterioration of comfort of an occupant of the vehicle.In view of this point, the pressure loss of the cooling water flowing into the predetermined tubes 21A can be increased in the heat exchanger 10 of the present embodiment because the openings of the one ends 21 aof the predetermined tubes 21A are partially closed by the closing member 50. As a result, a difference between the pressure loss of the cooling water flowing into the predetermined tubes 21A of the tubes 21 and the pressure loss of the cooling water flowing into other tubes of the tubes 21 disposed away from the inflow port 33 becomes small, so that it is possible to adjust the flows in the tubes 21.Further, it has been confirmed by the inventors that a protrusion 215 shown in an enlarged view in FIG. 5 is formed at an end 21 aof a pipe 21. The protrusion 215 is a burr or the like formed at the time of manufacturing the pipe 21. More specifically, the tube 21 is manufactured by cutting the tube product to the predetermined length as described above. A thickness of a portion of the tube product corresponding to the joint 214 of the tube 21 is greater than a thickness of the other portions of the tube product. At the joint 214 having such a large thickness, burr is likely to occur at the time of cutting the tube product. This causes the protrusion 215 to be formed at the one end 21 aof the tube 21.If the closure member 50 is simply formed in a flat plate shape, as shown in FIG. 7, the closure member 50 may be raised by the protrusion 215 of the tube 21 at the time of placing the closure member 50 on the one end 21 aof the tube 21. If a gap is formed between the one end 21 aof the pipe 21 and the closing member 50 by the raising of the closing member 50, an effect of closing the openings by the closing member 50 decreases, so that it becomes difficult to adjust the flows of the pipes 21.Therefore, as shown in FIG. 5, the closure member 50 of the present embodiment has a groove 51 formed on a surface 52 of the closure member 50 facing the one ends 21 aof the tubes 21. As shown in FIGS. 3 and 6, the groove 51 is formed to extend in the tube stacking direction X. Therefore, as shown in FIG. 5, when the closing member 50 is disposed at the one ends 21 aof the predetermined tubes 21A, the protrusion 215 of the predetermined tubes 21A is located in the groove 51 of the closing member 50. As a result, interference between the closure member 50 and the predetermined tubes 21A can be avoided. Therefore, a part of the openings of the one ends 21 aof the predetermined tubes 21A can be more reliably closed by the closing member 50. As described above, in the heat exchanger 10 of the present embodiment, the groove 51 corresponds to an avoiding structure for avoiding the interference between the protrusion 215 formed at the one ends 21 aof the predetermined tubes 21 and the closing member 50.According to the heat exchanger 10 of the present embodiment described above, the measures and effects described in the following (1) to (5) can be obtained.(1) The groove 51 formed in the closure member 50 can avoid the interference between the protrusion 215 formed at the one ends 21 aof the predetermined tubes 21A and the closure member 50. Therefore, it becomes difficult for the shutter member 50 to be raised by the protrusion 215. As a result, the one ends 21 aof the predetermined tubes 21A can be more surely closed by the closing member 50, so that an effect obtained by providing the closing member 50, i.e., uniformity of distribution of the cooling water in the tubes 21, can be more reliably improved.(2) If the protrusion 215 is formed at the one ends 21 aof the tubes 21, the closure member 50 may collide with the protrusion 215 of the predetermined tubes 21A at the time of inserting the closure member 50 into the first container 31 from the inflow port 33. As a result, it may be difficult to insert the shutter member 50. However, since the groove 51 is formed on the shutter member 50 as in the heat exchanger 10 of the present embodiment, the groove 51 can avoid the interference between the shutter member 50 and the protrusion 215 of the predetermined tubes 21A, and the groove 51 serves as a guide for the insertion of the shutter member 50. Further, an inner wall surface of the container 31 faces one end of the closure member 50 in the air flow direction Y, and the protrusions 215 of the tube 21 face the other end of the closure member 50 in the air flow direction Y. Displacement of the shutter member 50 in the air flow direction Y can be limited.(3) The groove 51 is formed on the surface 52 of the closing member 50 facing the one ends 21 aof the predetermined tubes 21A as the interference prevention structure between the closing member 50 and the protrusion 215 formed on the one ends 21 aof the predetermined tubes 21A. According to this configuration, the avoidance structure can be easily formed on the closure member 50.(4) The closing member 50 is provided so as to partially close the one ends 21 aof the predetermined tubes 21A. The closing member 50 has the groove 51 extending along protrusions 215 formed at the ends of the predetermined tubes 21A. According to this configuration, the one ends 21 aof the predetermined tubes 21A can be closed by a closing member 50, and interference between the closing member 50 and the protrusions 215 can be avoided.(5) The tubes 21 each have the metal plate 210 bent into the tube shape, and the metal plate 210 has the joint 214 at which both ends 212, 213 of the metal plate 210 are joined to the central portion of the metal plate 210. Since the tubes 21 having such a structure are likely to have the protrusion 215 formed of a burr or the like at the joint 214, the use of the above-described structure of the closure member 50 as in the present embodiment is of great importance.Modification: ModificationNext, a modification of the heat exchanger 10 of the first embodiment will be described.The shape of the groove 51 formed on the shutter member 50 can be changed appropriately. For example, as shown in FIG. 8, the shape of the groove 51 in a sectional plane perpendicular to the tube stacking direction X may be a recessed shape. Further, the groove 51 is not limited to a rectangular step as shown in FIG. 6, and may be formed in a convex curved shape as shown in FIG. 9.Further, as shown in FIG. 10, the groove 51 of the closure member 50 may be one of grooves 51 corresponding to the protrusions 215 at the one ends 21 aof the predetermined tubes 21A. According to such a configuration, it is possible to ensure strength of the closure part as compared with the case where the groove 51 is formed in an elongated hole shape shown in FIG. 6.Second EmbodimentNext, a heat exchanger 10 of a second embodiment will be described. Differences from the heat exchanger 10 of the first embodiment will be mainly described below.As shown in FIG. 11, a closure member 50 of the present embodiment has a through hole 54 that passes through the closure member 50 from one surface 52 facing the one ends 21 aof the tubes 21 to another surface 53 facing away from the one ends 21 aof the tubes 21. The through hole 54 is an elongated hole extending in the tube stacking direction X. Therefore, when the closing member 50 is disposed at the one ends 21 aof the predetermined tubes 21A, the protrusion 215 of the predetermined tubes 21A may be located in the through hole 54 of the closing member 50. As a result, interference between the shutter member 50 and the predetermined tube 21A can be avoided. Therefore, a part of the openings of the one ends 21 aof the predetermined tubes 21A can be more reliably closed by the closing member 50.According to the heat exchanger 10 of the present embodiment described above, measures and effects similar to or similar to those of the heat exchanger 10 of the first embodiment can be obtained.Modification: ModificationNext, a modification of the heat exchanger 10 of the second embodiment will be described.The shape of the through hole 54 formed on the closure member 50 can be changed appropriately. For example, as shown in FIG. 12, the through hole 54 of the closure member 50 may be one of through holes 54 corresponding to protrusions 215 at the one ends 21 aof the predetermined tubes 21A. According to such a configuration, it is possible to ensure strength of the closure member 50 as compared with the case where the through hole 54 is the elongated hole shown in FIG. 11.Other EmbodimentsThe present embodiments can be implemented in the following modes.The closing member 50 is not limited to a closing member that closes one ends 21 aof the tubes 21, but may also close one end 21 aof one tube 21. That is, the closure member 50 may be any closure member as long as the closure member closes an opening provided at an end of at least one of the tubes 21.The closing member 50 is not limited to a closing member that closes pipes disposed in the vicinity of the inflow port 33, and may be any closing member that closes one end 21 aof any pipe 21.In the heat exchanger 10 of each embodiment, the closing member 50 may be provided not in the first tank 31 but in the second tank 32 and partially close openings of the other ends 21 bof the tubes 21.The heat exchanger 10 of each embodiment is not limited to the heater core of the air conditioner, and may be applied to any heat exchanger.The present disclosure is not limited to the above specific examples. Those skilled in the art can appropriately change the above-described concrete examples, and these modifications are also included in the scope of the present disclosure as long as they have the features of the present disclosure. Each element included in each of the concrete examples described above and the placement, state, shape, and the like of the element are not limited to those illustrated, and may be changed as appropriate. The elements included in each of the concrete examples described above may be combined appropriately as long as there is no technical contradiction.

Claims

A heat exchanger (10) having tubes (21) arranged side by side and a tank (31) connected to ends (21a) of the tubes (21), the heat exchanger (10) performing heat exchange between a first fluid flowing inside the tubes (21) and a second fluid flowing outside the tubes (21), the heat exchanger (10) comprising: a closing member (50) arranged inside the tank (31) and partially closing an opening provided at an end (21a) of a predetermined tube (21A) that is at least one of the tubes (21), the predetermined tube (21A) having a protrusion (215) formed at the one end (21a) of the predetermined tube (21A), and the closing member (50) having an avoiding structure (51, 54), Avoiding interference between the protrusion (215) and the closure member (50), characterized in that the tubes (21) have a metal plate (210) bent in a tube shape, the metal plate (210) has a joint (214) at which both ends (212, 213) of the metal plate (210) are joined at a central portion of the metal plate (210), the protrusion (215) is formed at the joint (214), and the avoiding structure (51, 54) is formed at a position facing the joint (214).The heat exchanger (10) according to claim 1, wherein the avoiding structure (51, 54) is a groove (51) formed on a surface of the closing member (50) facing the end (21a) of the predetermined tube (21A).The heat exchanger (10) according to claim 2, wherein the predetermined tube (21A) is one of predetermined tubes (21A) having ends (21a) with openings partially closed by the closing member (50), and the groove (51) extends along protrusions (215) formed at the ends (21a) of the predetermined tubes (21A).The heat exchanger (10) according to claim 2, wherein the predetermined tube (21A) is one of predetermined tubes (21A) having ends (21a) with openings partially closed by the closing member (50), and the groove (51) is one of grooves (51) corresponding to protrusions (215) formed at the ends (21a) of the predetermined tubes (21A).The heat exchanger (10) according to claim 1, wherein the avoiding structure (51, 54) is a through hole (54) formed in the shutter member (50) such that the through hole (54) passes from one surface (52) facing the end (21a) of the predetermined tube (21A) to another surface (53) facing away from the end (21a) of the predetermined tube (21A).The heat exchanger (10) according to claim 5, wherein the predetermined tube (21A) is one of predetermined tubes (21A) having ends (21a) with openings partially closed by the closing member (50), and the through hole (54) extends along protrusions (215) formed at the ends (21a) of the predetermined tubes (21).The heat exchanger (10) according to claim 5, wherein the predetermined tube (21A) is one of predetermined tubes (21A) having ends (21a) with openings partially closed by the closing member (50), and the through hole (54) is one of through holes (54) corresponding to protrusions (215) formed at the ends (21a) of the predetermined tubes (21).

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