JP2007278556A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve pressure resistance of a header tank by preventing formation of a small clearance between header tank components. <P>SOLUTION: In this header tank 40 constituted by combining a tank member 50 having a circulating portion 51, a plate member 60 connected with a tube 10, and an intermediate layer material 70 disposed between the tank member 50 and the plate member 60, a recessed portion 71 formed by recessing a part corresponding to a base part of the circulating portion 51, is formed on a face opposite to the tank member 50, of the intermediate layer material 70. Thus the generation of a small clearance between the tank member 50 and the intermediate layer material 70 caused by the sagging shape of the base part of the circulating portion 51, is prevented, and the pressure resistance of the header tank 40 is improved. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a heat exchanger, and is suitable for application to a radiator of a supercritical refrigeration cycle apparatus, for example.

  Conventionally, Patent Document 1 discloses a heat exchanger applied to a radiator of a supercritical refrigeration cycle apparatus.

  As shown in FIG. 17, the header tank 40 that collects and distributes the refrigerant in the heat exchanger of Patent Document 1 includes a tank member 50 in which a circulation portion 51 that circulates fluid in the longitudinal direction of the header tank 40 is formed. The plate member 60 to which the plurality of tubes 10 are connected is combined.

  The circulation part 51 of the tank member 50 is formed by deforming a substantially central part in the width direction perpendicular to the longitudinal direction of the tank member 50 into a substantially U-shaped cross section, and by reducing the width dimension W, The load due to the pressure of the refrigerant flowing through the flow part 51 is suppressed from being concentrated in the direction in which the tank member 50 and the plate member 60 are about to separate (perpendicular to the surface where the flow part 51 is formed). Has improved.

Further, the plate member 60 has a connection portion 62 of the tube 10 bulging on the opposite side of the tank member 50 around the connection portion to which the tube 10 is connected. And a communication space for communicating with the communication portion 51 is formed.
JP 2003-314987 A

  By the way, the connection part 62 of the plate member 60 of patent document 1 is formed by press molding (refer paragraph 0063 of patent document 1), and generally the distribution | circulation part 51 of the tank member 50 is also formed by press molding. For this reason, a chamfered sagging shape portion X as shown in FIG. 18B is generated at the skirt portion of the connection portion 62 and the flow portion 51.

  18A is a longitudinal sectional view of the tank header 40 of Patent Document 1, and FIG. 18B is an enlarged view of a Y portion in FIG. 18A. More specifically, FIG. 18B is an enlarged view of the skirt portion of the connection portion 62.

  Therefore, when the tank member 50 and the plate member 60 of Patent Document 1 are combined and joined, a minute gap Z is formed in the vicinity of the sag shape portion X between the tank member 50 and the plate member 60. When pressure is applied in the header tank 40 in a state where such a minute gap Z is formed, stress concentrates in the minute gap Z, and the pressure resistance strength of the header tank 40 is significantly reduced.

  The present invention has been made in view of the above points, and it is an object of the present invention to prevent the formation of a minute gap between header tank constituent members and improve the pressure resistance of the header tank.

  In order to achieve the above object, the present invention includes a plurality of tubes (10) through which a fluid passes, and header tanks (40) disposed on both ends of the plurality of tubes (10), and the header tank (40). Are interposed between the plate member (60) to which the tube (10) is connected, the tank member (50) combined with the plate member (60), and the tank member (50) and the plate member (60). The intermediate layer material (70, 70a), and at least one of the tank member (50) and the plate member (60) swells on the opposite side of the intermediate layer material (70, 70a) and fluids inside. In the heat exchanger in which the bulging portion (51, 62) through which the gas flows is formed, the bulging portion (51, 62) is provided on the surface facing the bulging portion (51, 62) of the intermediate layer material (70, 70a). The part corresponding to the base part of Mase recesses (71, 71a, 72) and wherein the heat exchanger is formed.

  According to this, the site | part corresponding to the base part of a bulging part (51, 62) was dented in the bulging part (51, 62) opposing surface of an intermediate | middle layer material (70, 70a) (71, 71a, 72) is formed, the intermediate layer material (70, 70a), the tank member (50), the intermediate layer material (70, No minute gap is formed in the vicinity of the sag shape portion between 70a) and the plate member (60).

  As a result, even if pressure is applied to the header tank (40), stress does not concentrate in the minute gap, so that the pressure resistance strength of the header tank (40) can be improved.

  In the present invention, the portion corresponding to the skirt portion of the bulging portions (51, 62) is the bulging when the tank member (50), the plate member (60), and the intermediate layer material (70, 70a) are combined. This means a portion that overlaps the skirt portion of the bulging portion (51, 62) when viewed from the direction perpendicular to the formation surface of the protruding portion (51, 62).

  In addition, (71, 71a, 72) in the present invention does not mean only a portion recessed with respect to the reference plane, but also includes a portion excluding the portion. Therefore, (71, 71a, 72) is not only configured by changing the thickness of the intermediate layer material (70, 70a), but, for example, a through hole is made in the intermediate layer material (70, 70a). And those formed by excluding the intermediate layer material (70, 70a) corresponding to the base portion.

  Further, in the heat exchanger having the above-described characteristics, the bulging portion is specifically a circulation portion (51) formed in the tank member (50) and allowing fluid to flow in the longitudinal direction of the header tank (40). May be.

  Furthermore, the flow part (51) may be formed close to any one end side in the width direction perpendicular to the longitudinal direction of the tank member (50). According to this, as will be described in a fifth embodiment to be described later, since the flow portion (51) is approaching one end in the width direction of the tank member (50), for example, the tank member (50) It is easy to secure a flat surface (joint surface) for attaching a connector or the like to the outside.

  Furthermore, a plurality of flow sections (51) may be provided along the longitudinal direction of the tank member (50). According to this, it is possible to sufficiently secure the flow path cross-sectional area of the flow part (51) for flowing the fluid in the longitudinal direction of the header tank 40.

  Furthermore, the depth dimension (H) of the flow part (51) with respect to the flow part (51) formation surface of the tank member (50) is not less than the width dimension (W) of the flow part (51) on the flow part (51) formation surface. It may be the value of.

  By the way, the circulation part (51) of the tank member (50) needs to have an appropriate flow path cross-sectional area so as not to increase the pressure loss when the fluid passes. If the depth dimension (H) of the flow part (51) is equal to or greater than the width dimension (W) as in the present invention, the depth dimension (H) is less than the width dimension (W). On the other hand, even if the width dimension (W) is reduced, an appropriate flow path cross-sectional area can be ensured.

  And if a width dimension (W) can be made small, the load concerning the direction perpendicular | vertical to the flow part (51) formation surface of a tank member (50) among the loads by the pressure of the fluid which distribute | circulates a flow part (51) can be made small. As a result, the load in the direction in which the tank member (50) and the plate member (60) are about to be separated (perpendicular to the formation surface of the flow part (51)) can be reduced, so that the pressure resistance of the header tank (40) is improved. be able to.

  In the heat exchanger having the above-described characteristics, the bulging portion may be specifically a connection portion (62) formed on the plate member (60) and connected to the tube (10).

  In the heat exchanger having the above-described characteristics, the intermediate layer material (70) may be provided with a communication hole (72) that allows the inside of the tube (10) to communicate with the tank member (50) side. According to this, the communication space which connects reliably the inside of a tube (10) and the tank member (50) side by the internal space of a communicating hole (72) can be formed.

  In the heat exchanger having the above characteristics, the intermediate layer material (70) may be provided with a position restricting portion (74) for restricting the connection position of the tube (10). According to this, since the connection position of the tube (10) can be positioned easily and appropriately, the heat exchanger having the above-described characteristics can be easily manufactured.

  Moreover, in the heat exchanger having the above-described characteristics, the intermediate layer material (70) may be configured as a separate member separate from the tank member (50) and the plate member (60). According to this, since the intermediate layer material (70) is composed of a separate member separate from the tank member (50) and the plate member (60), the intermediate layer material (70) can be easily recessed (71). ) Can be configured.

  Furthermore, the intermediate layer material (70) constituted by a member different from the tank member (50) and the plate member (60) may be formed of a bare material whose surface is not clad with a brazing material. According to this, the manufacturing cost of the intermediate layer material (70) can be reduced.

  Furthermore, the intermediate layer material (70) configured as a member different from the tank member (50) and the plate member (60) may be formed by press molding or may be formed by extrusion molding. According to this, the manufacturing cost of an intermediate | middle layer material (70) can be reduced further.

  In the heat exchanger having the above-described characteristics, at least one of the tank member (50), the plate member (60), and the intermediate layer material (70) is temporarily attached to at least one of the other constituent members. Fixed temporary fixing parts (52, 64, 65, 76) may be provided. According to this, since the structural members (50, 60, 70) constituting the header tank (40) can be joined in a temporarily fixed state, the heat exchanger having the above-described characteristics can be easily manufactured.

  In the heat exchanger having the above-described features, the intermediate layer material (70) may be configured by bending at least one predetermined portion of the tank member (50) and the plate member (60). According to this, since the temporary fixing process of temporarily fixing the intermediate layer material (70) to the tank member (50) and the plate member (60) can be omitted, the manufacturing cost of the heat exchanger can be reduced.

  In addition, you may employ | adopt specifically the both ends of the width direction perpendicular | vertical to the longitudinal direction of a tank member (50) and a plate member (60) etc. as a predetermined site | part.

  Moreover, in the heat exchanger having the above-described features, the plurality of tubes (10) are stacked and arranged along the longitudinal direction of the header tank (40), and the row in which the plurality of tubes (10) are stacked is A plurality may be provided. According to this, since a plurality of heat exchange parts (core parts) formed by arranging the plurality of tubes (10) in a stacked manner can be formed, the heat exchange performance of the entire heat exchanger can be improved. .

Further, in the heat exchanger having the above-described characteristics in which a plurality of stacked arrangement rows of tubes (10) are provided, the header tank (40) includes a tank member (50), a plate member (60), and an intermediate layer material (70). A through hole (43) may be provided to penetrate through. According to this, the dew condensation water etc. which were stored between each row | line | column with which the some tube (10) was laminated | stacked can be drained easily. Moreover, the lamination | stacking arrangement row | line | column of the tube (10) was provided with two or more. In the heat exchanger having the characteristics described above, the intermediate layer material (70) may be provided with a communication path (75) that allows the tubes (10) arranged in different rows to communicate with each other. According to this, the tubes (10) stacked and arranged in different rows can be easily communicated without adding dedicated piping or the like.

  Further, in the heat exchanger having the above characteristics, the fluid may be carbon dioxide. That is, the heat exchanger having the above-described characteristics may be applied to a supercritical refrigeration cycle apparatus in which the fluid (refrigerant) pressure exceeds the critical pressure.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

(First embodiment)
A first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is an overall configuration diagram of a heat exchanger according to the present embodiment. This heat exchanger is a radiator 1 (gas cooler) that exchanges heat between refrigerant and air in a vehicle air conditioner to dissipate the refrigerant. Therefore, the fluid in this embodiment is a refrigerant.

  The vehicle air conditioner of the present embodiment constitutes a supercritical refrigeration cycle in which the high-pressure side pressure is equal to or higher than the critical pressure (supercritical state), and employs carbon dioxide as the refrigerant. Of course, ethylene, ethane, nitric oxide or the like may be employed as the refrigerant. Note that the directions of the up, down, left and right arrows in FIG. 1 indicate the directions viewed from the front of the vehicle when mounted on the vehicle.

  In the radiator 1, a large number of tubes 10 through which a refrigerant flows are stacked, and fins 20 that promote heat exchange between the refrigerant and air are disposed between adjacent tubes 10. The tube 10 and the fin 20 constitute a substantially rectangular core portion 11 that forms a heat exchange portion.

  Each tube 10 is a single-hole or multi-hole tube having a flat cross section, and the plurality of tubes 10 are arranged in parallel at a predetermined interval so that their flat surfaces are parallel. ing. Air that exchanges heat with the refrigerant flows from the front to the rear of the vehicle, and flows from the front to the back in FIG.

  A pair of header tanks 40 that collect and distribute refrigerant are connected to both ends in the longitudinal direction of the tube 10. The header tank 40 is a substantially cylindrical hollow member extending in the stacking direction of the tubes 10 (vertical direction in FIG. 1). The plate member 60 to which the tube 10 is connected, the tank member 50 combined with the plate member 60, and the tank member 50. This is a so-called split type header tank configured to include an intermediate layer material 70 interposed between the plate member 60 and the plate member 60.

  Details of the header tank 40 will be described with reference to FIG. 2A is a cross-sectional view taken along the line AA in FIG. 1, and FIG. 2B is a cross-sectional view taken along the line BB in FIG. More specifically, FIG. 2A is a cross-sectional view of a position where the tube 10 is inserted, and FIG. 2B is a cross-sectional view of a position where the tube 10 is not inserted.

  For clarity, the hole in the tube 10 is omitted in FIG. 2A, and the fin 20 is not shown in FIG. 2B. The same applies to the illustration of cross-sectional views in the following embodiments.

  First, the tank member 50 is formed by deforming an elongated plate-like aluminum alloy clad with a brazing material, and deforms a substantially central portion in a width direction perpendicular to the longitudinal direction into a substantially U-shaped cross section. The circulation portion 51 is configured, and a temporary fixing portion 52 is formed by bending both end portions in the width direction toward the plate member 60 and the intermediate layer material 70 by about 90 °.

  The circulation part 51 swells on the opposite side of the intermediate layer material 70 and causes the refrigerant to circulate in the longitudinal direction of the header tank 40 in the inner space. Therefore, the circulation part 51 is a bulging part in the present embodiment. Furthermore, as shown in FIG. 2A, the depth dimension H of the flow part 51 with respect to the flow part 51 formation surface is a value equal to or larger than the width dimension W of the flow part 51 on the flow part 51 formation surface.

  The temporary fixing portion 52 temporarily fixes the tank member 50, the plate member 60, and the intermediate layer material 70 before the tank member 50 and the plate member 60 are joined and integrated. Specifically, as shown in FIG. 2, with the intermediate layer material 70 sandwiched between the tank member 50 and the plate member 60, the temporary fixing portion 52 is bent along the outer periphery of the plate member 60. Temporary fixing is made by tightening.

  Since the tank member 50, the plate member 60, and the intermediate layer material 70 can be joined in a state of being temporarily fixed at appropriate positions by the temporary fixing portion 52, the dimensional accuracy and assembly accuracy of the header tank 40 can be improved, and heat dissipation can be achieved. The productivity of the container 1 can be improved. Such a shape of the tank member 50 can be easily formed by press molding.

  Next, the plate member 60 is formed by deforming an elongated plate-like aluminum alloy clad with a brazing material, and the length in the longitudinal direction is substantially the same as that of the tank member 50. Further, the plate material 60 has a plurality of slit holes 61 having a shape that fits the flat cross section of the tube 10. The same number of the slit holes 61 as the tubes 10 are provided, and the distal ends of the tubes 10 are joined in a state of being inserted into the slit holes 61.

  Next, the intermediate layer material 70 is composed of a separate member separate from the tank member 50 and the plate member 60. Specifically, the intermediate layer material 70 is in the form of an elongated plate that is not clad with a brazing material. Made of a bare material of aluminum alloy. Further, the length in the longitudinal direction is substantially the same as that of the tank member 50.

  Further, the intermediate layer material 70 communicates the inside of the tube 10 and the circulation portion 51 of the tank member 50 to a portion corresponding to the slit hole 61 of the plate member 60 and a concave portion 71 having a concave surface facing the tank member 50 side. And a communication hole 72 to be made.

  The recesses 71 are provided in two rows along portions corresponding to both sides of the skirt portion of the flow part 51, and when viewed from a direction perpendicular to the flow part 51 formation surface of the tank member 50, the flow part 51. It arrange | positions so that the sagging shape part vicinity formed in the base part of this and the recessed part 71 may overlap.

  The angle between the side surface of the recess 71 and the surface of the tank member 50 where the flow part 51 is formed is about 90 °, and the inside of the communication hole 72 allows the tube 10 and the flow part 51 to communicate with each other. A communication space 73 is formed.

  In the present embodiment, as described above, since the intermediate layer material 70 is configured as a separate part with respect to the tank member 50 and the plate member 60, such a shape can be easily formed by press molding and extrusion molding. Furthermore, since the bare material in which the brazing material is not clad is employed, the manufacturing cost can be reduced.

  In addition, when forming by extrusion molding, after forming the recessed part 71, pulling out to a longitudinal direction, what is necessary is just to form the communicating hole 72 by press work or punching.

  As shown in FIG. 1, a tank cap 80 for closing the upper and lower ends of the header tank 40 is joined to the upper end and the lower end of the header tank 40. Further, one of the pair of header tanks 40 (left header tank in FIG. 1) is provided with a first connector 91 for connecting a refrigerant inflow pipe (not shown) for allowing the refrigerant to flow into the radiator 1 and the refrigerant. A second connector 92 for connecting a refrigerant outflow pipe (not shown) that flows out of the radiator 1 is joined.

  Specifically, the first and second connectors 91 and 92 are joined to a through hole (not shown) provided on the outer peripheral surface of the tank member 50 in a state of being temporarily fixed by caulking or the like. It is arranged so as to protrude in the direction perpendicular to the longitudinal direction of 40 and the longitudinal direction of the tube 10.

  In addition, a separator 42 is disposed inside the header tank 40 to which the first and second connectors 91 and 92 are joined, and a circulation portion 51 of the header tank 40 is divided into two parts, an upper side and a lower side. Furthermore, side plates 30 that extend in parallel with the tube 10 and reinforce the core portion 11 are disposed on both ends in the stacking direction of the tube 10.

  In the radiator 1 of the present embodiment, all the components except for the intermediate layer material 70 are made of aluminum alloy in which a brazing material is clad, and these components are made by caulking, a dedicated jig, or the like. In the temporarily fixed state, they are joined together by brazing.

  Here, “brazing” is a technique for joining so as not to melt the base material using brazing material or solder, as described in, for example, “Connection / Joint Technology” (Tokyo Denki University Press). Say. More specifically, when joining using a filler material (brazing material) having a melting point of 450 ° C. or higher is called brazing, and when joining using a filler material (solder) having a melting point of less than 450 ° C. This is called soldering. In this embodiment, they are joined together by “brazing” of brazing.

  The radiator 1 of the present embodiment has the above-described configuration, and the refrigerant flows in the radiator 1 as follows. First, the refrigerant whose pressure is increased to a critical pressure or higher in a compressor (not shown) of the vehicle air conditioner is above the header tank 40 (the left header tank in FIG. 1) via the first connector 91 of the radiator 1. Flows into the circulation part 51 of the.

  The refrigerant that has flowed from the first connector 91 into the circulation portion 51 on the upper side of the header tank 40 moves the tube 10 disposed above the separator 42 from the left side to the right side, thereby moving the header tank 40 on the opposite side (on the right side in FIG. 1). Into the header tank).

  Further, the refrigerant that has flowed into the header tank 40 on the opposite side moves down the circulation part 51, moves the tube 10 arranged below the separator 42 from the right side to the left side, and is connected to the second connector 92. It moves to the flow part 51 below the header tank 40 and flows out from the second connector 92 to the upstream side of the expansion valve (not shown). The refrigerant radiates heat by exchanging heat with air while passing through the tube 10.

  By the way, since the refrigerant | coolant (carbon dioxide) of this embodiment is a supercritical state as mentioned above, the refrigerant | coolant which flows in into the heat radiator 1 becomes a high voltage | pressure (specifically 7 Mpa or more). Therefore, the header tank 40 of the radiator 1 is required to have pressure resistance that can withstand this refrigerant pressure.

  Therefore, in the radiator 1 of the present embodiment, the flow portion 51 of the header tank 40 is formed by deforming the central portion in the width direction of the tank member 50 into a substantially U-shaped cross section, and the width dimension W of the flow portion 51 is set. By reducing the size, the load due to the pressure of the refrigerant flowing through the flow part 51 is avoided from being concentrated in the direction in which the tank member 50 and the plate member 60 are about to be separated (perpendicular to the flow part 51 forming surface). The pressure resistance of the tank 40 is improved.

  Furthermore, according to the structure of the heat radiator 1 of this invention, the following outstanding effects are also exhibited. First, in the radiator 1 according to the present invention, the recess 71 is formed in the surface of the intermediate layer material 70 facing the tank member 50 so as to have a recess corresponding to the skirt portion of the flow portion 51. Even if a sagging shape occurs in the portion, it is possible to prevent a minute gap from being formed in the vicinity of the sagging shape portion between the intermediate layer material 70 and the tank member 50.

  As a result, even if pressure is applied in the header tank 40, stress concentration in the minute gap does not occur, so the pressure strength of the header tank 40 can be improved.

  Furthermore, since the depth dimension H of the flow part 51 of this embodiment is a value greater than or equal to the width dimension W, the width dimension W is set after setting the flow path cross-sectional area of the flow part 51 to an appropriate value. Can be small. As a result, the load applied in the direction perpendicular to the flow portion 51 formation surface among the loads due to the pressure of the refrigerant flowing through the flow portion 51 can be further reduced, and the pressure resistance of the header tank 40 can be further improved.

  Furthermore, since the intermediate layer material 70 of the present embodiment is provided with a communication hole 72 that allows the inside of the tube 10 and the flow portion 51 to communicate with each other, a communication space 73 is formed by the internal space of the communication hole 72 to form the tube 10. The inside and the circulation part 51 can be reliably communicated.

(Second Embodiment)
In the first embodiment, the recesses 71 of the intermediate layer material 70 are formed in two rows along portions corresponding to both sides of the skirt portion of the flow part 51. However, in this embodiment, as shown in FIG. Are formed in only one row. 3A is a cross-sectional view taken along the line AA of FIG. 1 in the present embodiment, and FIG. 3B is a cross-sectional view taken along the line BB of FIG.

  The recesses 71 of the present embodiment are provided in only one row along the outer side of the formation part of the flow part 51 of the tank member 50 including the skirt portions on both sides of the flow part 51, but as in the first embodiment, When viewed from the direction perpendicular to the flow portion 51 formation surface, the vicinity of the sag shape portion formed at the skirt portion of the flow portion 51 and the concave portion 71 are arranged so as to overlap. Other configurations of the radiator 1 are the same as those in the first embodiment.

  Therefore, also in the heat radiator 1 of this embodiment, while being able to acquire the effect similar to 1st Embodiment, the weight reduction effect of the intermediate | middle layer material 70 can also be acquired.

(Third embodiment)
In the first embodiment, the substantially flat plate member 60 is employed. However, in the present embodiment, as shown in FIGS. 4 and 5, the tube 10 is connected to the slit hole 61 forming portion of the plate member 60. A connecting portion 62 is formed. 4 is a longitudinal sectional view of the header tank 40 in the present embodiment, FIG. 5 (a) is a sectional view taken along line AA in FIG. 4, and FIG. 5 (b) is a sectional view taken along line BB in FIG. FIG. More specifically, FIG. 4 is a cross-sectional view taken along the line CC of FIG.

  The connecting portion 62 swells on the opposite side of the intermediate layer material 70, and a slit hole 61 similar to that of the first embodiment is formed at the top. More specifically, a plurality of connecting portions 62 are formed so as to extend in the width direction of the plate member 60 along the flat surfaces on both sides of the tube 10.

  In addition, a communication space 63 that connects the inside of the tube 10 and the circulation portion 51 is also formed in the internal space of the connection portion 62. Therefore, the connection part 62 is a bulging part of this embodiment. Such a shape of the plate member 60 can be easily formed by press molding.

  Furthermore, the communication hole 72 of the intermediate layer material 70 of the present embodiment is formed along the outside of the connection portion 62 forming portion including the skirt portion of each connection portion 62. Therefore, when viewed from a direction perpendicular to the connection portion 62 forming surface, the communication hole 72 is disposed so as to overlap the vicinity of the sag shape portion formed in the skirt portion of the connection portion 62. In addition, the angle between the side surface of the communication hole 72 and the connection part 62 formation surface of the plate member 60 is about 90 degrees.

  Other configurations of the radiator 1 are the same as those in the first embodiment. Therefore, also in the heat radiator 1 of this embodiment, the effect similar to 1st Embodiment can be acquired.

  Further, even if the connection portion 62 is formed on the plate member 60 side as in the present embodiment, the communication hole 72 is formed in a portion corresponding to the skirt portion of the connection portion 62 on the surface facing the plate member 60 of the intermediate layer material 70. Therefore, substantially the same effect as in the case where the recess corresponding to the bottom portion of the connection portion 62 is formed by the communication hole 72 can be obtained. Accordingly, the communication hole 72 also functions as a recess in the present embodiment.

  Thereby, even if a sagging shape occurs in the skirt portion of the connecting portion 62, it is possible to prevent a minute gap from being formed in the vicinity of the sagging shape portion between the intermediate layer material 70 and the plate member 60. As a result, even if pressure is applied in the header tank 40, stress concentration in the minute gap does not occur, so the pressure strength of the header tank 40 can be improved.

  Furthermore, in this embodiment, since the communication spaces 63 and 73 that allow the inside of the tube 10 to communicate with the circulation portion 51 can be formed by the internal spaces of the connection portion 62 and the communication hole 72, a sufficient communication space is ensured, and the refrigerant Pressure loss when flowing in and out between the tube 10 and the flow part 51 can also be reduced.

(Fourth embodiment)
In 4th Embodiment, the position control part 74 which controls the connection position of the tube 10 is provided in the intermediate | middle layer material 70 of 1st Embodiment. Other configurations of the radiator 1 are the same as those in the first embodiment. Details of the position restricting portion 74 provided in the intermediate layer material 70 will be described with reference to FIG. 6 is a cross-sectional view taken along the line AA of FIG. 1 in the present embodiment.

  As shown in FIG. 6, the position restricting portion 74 is formed at the end of the communicating hole 72 on the tank member 50 side so as to protrude inside the communicating hole 72. Accordingly, when the tube 10 is inserted into the slit hole 61 of the plate member 60, if the tube 10 is inserted until the distal end of the tube 10 contacts the position defining portion 74, the connection position of the tube 10 is determined. Other configurations of the radiator 1 are the same as those in the first embodiment.

  Therefore, in the radiator 1 of the present embodiment, the same effect as that of the first embodiment can be obtained, and positioning when the tube 10 is inserted into the slit hole 61 of the plate member 60 is facilitated. The productivity of (heat radiator 1) can also be improved.

(Fifth embodiment)
In the first embodiment, the flow part 51 is formed at a substantially central part in the width direction of the tank member 50. However, in this embodiment, the flow part 51 is formed in the width direction of the tank member 50 as shown in FIG. It is formed close to either one end side. In the present embodiment, specifically, the tank member 50 is formed close to the vehicle rear side end in the width direction.

  7A is a cross-sectional view taken along line A′-A ′ of FIG. 1 in the present embodiment, and FIG. 7B is a cross-sectional view taken along line BB of FIG. 1. More specifically, FIG. 7A is a cross-sectional view of the position where the tube 10 is inserted in the vicinity of the first connector 91.

  Furthermore, the intermediate layer material 70 of the present embodiment is disposed only on the end portion side where the flow portion 51 is not formed, and the communication hole 72 of the present embodiment is the end portion of the intermediate layer material 70 on the flow portion 51 side. Is formed into a comb-teeth shape by cutting it into a U-shape.

  Moreover, since the site | part corresponding to the skirt part of the distribution part 51 is excluded among the tank member 50 opposing surfaces of the intermediate | middle layer material 70, the site | part corresponding to the skirt part of the distribution part 51 was substantially dented. The same effect as when the recess is formed can be obtained. Accordingly, the communication hole 72 also functions as a recess in the present embodiment. Other configurations of the radiator 1 are the same as those in the first embodiment.

  Therefore, also in the heat radiator 1 of this embodiment, while being able to acquire the effect similar to 1st Embodiment, the weight reduction effect of the intermediate | middle layer material 70 can also be acquired.

  Furthermore, by forming the flow part 51 close to one end in the width direction of the tank member 50, it becomes easy to secure the joining surface 53 for joining the first connector 91 to the outside of the tank member 50. The joining strength of the one connector 91 can be improved. Of course, the same effect can be obtained for the second connector 92 and other tank member 50 joining parts (specifically, a bracket (not shown) or the like).

(6th Embodiment and 7th Embodiment)
In the first to fifth embodiments, the intermediate layer material 70 is configured as a separate member separate from the tank member 50 and the plate member 60, but in this embodiment, the intermediate layer material 70 a is configured as the tank member 50. In addition, at least one predetermined portion of the plate member 60 is bent.

  In the sixth embodiment, as shown in FIG. 8, specifically, the intermediate layer material 70 a is integrally formed with the plate member 60 by bending both end portions 71 a in the width direction of the plate member 60. 8A is a cross-sectional view taken along line AA in FIG. 1 according to the sixth embodiment, and FIG. 8B is a cross-sectional view taken along line BB in FIG.

  Further, the intermediate layer material 70a has both end portions 71a so that the intermediate layer material 70a and the skirt portion of the flow portion 51 do not overlap when viewed from a direction perpendicular to the flow portion 51 formation surface of the tank member 50. Since it is configured to be bent, it is possible to obtain substantially the same effect as in the case where the intermediate layer material 70a is formed with a concave portion in which a portion corresponding to the skirt portion of the flow portion 51 is recessed. Therefore, both end portions 71a also serve as a concave portion in the present embodiment.

  Further, since the intermediate layer material 70 a is formed by folding back both end portions 71 a of the plate member 60, the intermediate layer material 70 a has a thickness corresponding to the thickness of the plate member 60. Accordingly, a communication space 73 that allows the inside of the tube 10 to communicate with the flow portion 51 is formed by the space formed between the both end portions 71a. Other configurations of the radiator 1 are the same as those in the first embodiment.

  Therefore, in the radiator 1 of the sixth embodiment, the same effect as that of the first embodiment can be obtained, and the temporary fixing step of temporarily fixing the intermediate layer material 70a to the plate member 60 can be omitted. The manufacturing cost of the vessel can be reduced.

  Furthermore, in the seventh embodiment, as shown in FIG. 9, specifically, the intermediate layer material 70 a is integrally formed with the tank member 50 by bending both end portions in the width direction of the tank member 50. 9A is a cross-sectional view taken along line AA in FIG. 1 according to the seventh embodiment, and FIG. 9B is a cross-sectional view taken along line BB in FIG.

  In addition, since the intermediate layer material 70a is configured by both end portions in the width direction of the tank member 50, in the present embodiment, the temporary fixing portions 52 of the tank member 50 are arranged and are disposed at both end portions in the width direction of the plate member 60. A temporary fixing portion 64 for temporarily fixing the plate member 60 to the tank member 50 is formed. Other configurations of the radiator 1 are the same as those in the sixth embodiment. Therefore, also in the heat radiator 1 of 7th Embodiment, the effect similar to 6th Embodiment can be acquired.

(Eighth embodiment)
In the above-described embodiment, the example in which one circulation portion 51 of the tank member 50 is provided along the longitudinal direction of the header tank 40 has been described. However, in this embodiment, as shown in FIG. A plurality (specifically, two rows) are provided along the longitudinal direction of 40. 10 is a cross-sectional view taken along line AA of FIG. 1 in the present embodiment. Other configurations are the same as those of the second embodiment.

  Therefore, also in the heat radiator 1 of this embodiment, while being able to acquire the same effect as 2nd Embodiment, the flow-path cross-sectional area of the distribution | circulation part 51 which distribute | circulates the fluid to the longitudinal direction of the header tank 40 is ensured enough. And since the pressure loss at the time of a refrigerant | coolant passing the distribution part 51 can be reduced, the performance improvement of a heat exchanger can be aimed at.

(Ninth embodiment)
In the above-described embodiment, the example of the heat exchanger (heat radiator 1) in which the tubes 10 are stacked in only one row along the longitudinal direction of the header tank 40 has been described. However, in this embodiment, the tubes 10 are stacked in a plurality of rows. The heat exchanger will be described.

  FIG. 11 is an overall perspective view of the heat exchanger of the present embodiment. This heat exchanger is an evaporation that evaporates the refrigerant by exchanging heat between the refrigerant and air in the same vehicle air conditioner as in the first embodiment. This is vessel 2. Therefore, the fluid in this embodiment is also a refrigerant (carbon dioxide). In addition, each direction of the up / down / left / right arrows in FIG. 11 indicates a direction viewed from the front of the vehicle in the vehicle mounted state.

  In the evaporator 2, the tubes 10 and the fins 20 are stacked in two rows in parallel in the longitudinal direction of the header tank 40 (the left-right direction in FIG. 11). Accordingly, two core portions 11 are also configured. In addition, since the air that exchanges heat with the refrigerant flows from the front to the rear of the vehicle, the two core portions 11 are arranged in series with respect to the air flow (arrow D).

  Similarly to the first embodiment, split type header tanks 40 are connected to both ends in the longitudinal direction of the tube 10. The header tank 40 of this embodiment also has a tank member 50, a plate member 60, and an intermediate layer material 70, and has a shape that extends in the stacking direction of the tubes 10 (the left-right direction in FIG. 11).

  Details of the header tank 40 will be described with reference to FIGS. FIG. 12 is a schematic exploded perspective view of the tube 10 and the header tank 40 (specifically, the tank member 50, the plate member 60, and the intermediate layer material 70). In FIG. 12, the communication hole 72 of the intermediate layer material 70 is shown only by a broken line for the sake of clarity of illustration, and the detailed shape is omitted.

  13A is a longitudinal sectional view in the longitudinal direction of the header tank 40 including the line EE in FIG. 12, and FIG. 13B is a longitudinal direction of the header tank 40 including the line FF in FIG. It is a vertical sectional view. More specifically, FIG. 13A is a cross-sectional view of a position where the tube 10 is inserted, and FIG. 13B is a cross-sectional view of a position where the tube 10 is not inserted.

  The tank member 50, the plate member 60, and the intermediate layer material 70 of the present embodiment are basically formed in the same manner as in the first embodiment, except for the following points. First, the circulation portions 51 of the tank member 50 are formed in two rows in the longitudinal direction so as to match the stacked arrangement row of the tubes 10. In the following description, in the two rows of circulation portions 51, the upstream flow portion (arrow D) upstream flow portion is the leeward flow portion 51a, and the downstream air flow direction (arrow D) flow portion is the leeward circulation. It is called part 51b.

  Next, the slit hole 61 of the plate member 60 is arrange | positioned so that it may match with each tube 10 laminated | stacked and arranged in 2 rows.

  Next, the recesses 71 of the intermediate layer material 70 are also formed in four rows (= 2 rows × 2) along portions corresponding to both sides of the skirt portion of the leeward flow portion 51a and the leeward flow portion 51b. Further, the communication holes 72 are also provided at portions corresponding to the slit holes 61 of the plate member 60.

  Further, in the present embodiment, different rows are arranged in predetermined portions (on the right side of the intermediate layer material 70 in FIG. 12) of the intermediate layer material 70 of one of the pair of header tanks 40 (upper header tank in FIG. 11). A communication path 75 is provided for communicating the communication holes 72 corresponding to the tubes 10 stacked on each other.

  The communication path 75 will be described with reference to FIG. FIG. 14 is a vertical cross-sectional view in the longitudinal direction of the header tank 40 at a position where the tube 10 is inserted in a portion where the communication path 75 is formed in the intermediate layer material 70. That is, it is a longitudinal direction vertical sectional view of the header tank 40 including the GG line of FIG. As shown in FIG. 14, the communication passages 75 allow the tubes 10 arranged in different rows to communicate with each other.

  Next, tank caps 80 for closing the left and right end portions of the header tank 40 are joined to the left and right end portions of the header tank 40 as shown in FIG. Furthermore, a predetermined tank cap 80 (on the right side of the upper header tank 40 in FIG. 11) radiates the refrigerant with the first connector 91 for connecting a refrigerant inflow pipe (not shown) through which the refrigerant flows into the radiator 1. A second connector 92 for connecting a refrigerant outflow pipe (not shown) that flows out of the container 1 is provided.

  Specifically, the first connector 91 is disposed so as to communicate with the leeward circulation portion 51b, and the second connector 92 is disposed so as to communicate with the leeward circulation portion 51a, both of which are parallel to the longitudinal direction of the header tank 40. It is arranged to protrude in the direction.

  A separator 42 is disposed inside the header tank 40 to which the first and second connectors 91 and 92 are joined, and the circulation portions 51a and 51b of the header tank 40 are divided into two parts on the left side and the right side. Accordingly, the first connector 91 communicates with the right side of the leeward circulation part 51b, and the second connector 92 communicates with the right side of the leeward circulation part 51a. Further, the communication path 75 of the intermediate layer material 70 is provided so as to allow the flow portions 51 a and 51 b on the left side of the separator 42 of the intermediate layer material 70 to communicate with each other.

  Side plates 30 that extend in parallel with the tubes 10 and reinforce the core portions 11 are disposed on both ends in the stacking direction of the tubes 10. Similarly to the first embodiment, the evaporator 2 of the present embodiment is formed by forming each component member from an aluminum alloy clad with a brazing material and integrally joining the components by brazing.

  Since the evaporator 2 of the present embodiment has the above configuration, the refrigerant flows through the evaporator 2 as indicated by arrows a to i in FIG. First, the refrigerant that has flowed out of the expansion valve (not shown) flows from the first connector 91 to the right side of the leeward circulation portion 51b of the header tank 40 (upper header tank in FIG. 11) (arrow a).

  The refrigerant flowing from the first connector 91 to the right side of the leeward circulation part 51b moves from the upper side to the lower side of the tube 10 disposed on the right side of the separator 42 to move to the opposite side header tank 40 (the lower side of FIG. 11). Into the header tank (arrow b).

  The refrigerant flowing into the header tank 40 on the opposite side moves to the left side of the leeward circulation part 51b (arrow c), moves the tube 10 arranged on the left side of the separator 42 from the lower side to the upper side, and moves to the upper header. It flows into the left side of the leeward flow part 51b of the tank 40 (arrow d).

  The refrigerant that has flown into the left side of the leeward circulation portion 51b of the upper header tank 40 flows into the left side of the leeward circulation portion 51a through the communication path 75 (arrow e). The refrigerant that has flowed into the left side of the windward flow portion 51a moves from the upper side to the lower side of the tube 10 disposed on the left side of the separator 42 and flows into the header tank 40 on the opposite side (arrow f).

  The refrigerant flowing into the header tank 40 on the opposite side moves to the right side of the windward flow part 51a (arrow g), and moves the tube 10 disposed on the right side of the separator 42 from the upper side to the lower side to move to the second connector. It flows into the right side upflow part 51b right side of the header tank 40 to which 92 is connected (arrow h). The refrigerant that has flowed to the right side of the windward flow part 51b flows from the second connector 92 into an accumulator on the suction side of a compressor (not shown) (arrow i). When the refrigerant passes through the tube 10, the refrigerant absorbs heat from the air and evaporates.

  By the way, even if it is the evaporator 2, if a failure of an expansion valve (not shown) etc. generate | occur | produces, an inside may become a high voltage | pressure. For this reason, the header tank 40 of the evaporator 2 is required to have a predetermined pressure resistance.

  In the evaporator 2 of the present invention, the concave portion 71 is formed on the surface facing the tank member 50 of the intermediate layer material 70. The concave portions 71 are formed by denting the portions corresponding to the skirt portions of the circulation portions 51a and 51b. Even if a sagging shape is generated at the skirt portion, it is possible to prevent a minute gap from being formed in the vicinity of the sagging shape portion between the intermediate layer material 70 and the tank member 50.

  As a result, even if pressure is applied in the header tank 40, stress concentration in the minute gap does not occur, so the pressure strength of the header tank 40 can be improved.

  Furthermore, the evaporator 2 according to the present embodiment is not simply a diversion of the radiator 1 according to the first embodiment, and is provided with a plurality of rows in which the tubes 10 are stacked. A plurality of the refrigerants can be formed in series, and the refrigerant can be efficiently evaporated in the core part 11 on the leeward side and the core part 11 on the leeward side. As a result, the heat exchange performance of the entire heat exchanger can be improved.

  Further, the intermediate layer material 70 of the present embodiment is provided with a communication path 75 that allows the tubes 10 arranged in different rows to communicate with each other, so that the tubes 10 arranged in different rows communicate with each other. There is no need to add special piping. As a result, a heat exchanger having a plurality of core portions 11 can be easily manufactured without increasing the manufacturing cost and increasing the size.

(10th Embodiment)
In the present embodiment, a through hole 43 that penetrates the tank member 50, the plate member 60, and the intermediate layer material 70 is configured in the header tank 40 of the heat exchanger (evaporator 2) of the ninth embodiment. Details of the through hole 43 will be described with reference to FIG. FIG. 15 is a vertical cross-sectional view in the longitudinal direction of the header tank 40 where the through hole 43 is provided.

  The through hole 43 is configured between the leeward flow portion 51a and the leeward flow portion 51b, and is provided so as to penetrate the tank member 50, the plate member 60, and the intermediate layer material 70 coaxially. The hole shape of the through hole 43 may be circular or polygonal.

  According to the evaporator 2 of the present embodiment, the same effects as those of the ninth embodiment can be obtained, and the condensed water and the like stored between the rows in which the tubes 10 are stacked are easily drained. Can do.

(Eleventh embodiment)
In the present embodiment, a temporary fixing hole 54 is provided in the tank member 50 of the header tank 40 of the heat exchanger (evaporator 2) of the ninth embodiment, and the temporary fixing hole is further provided in the plate member 60 and the intermediate layer material 70. Claw portions 65 and 76 that are temporarily fixed to 54 are provided. Therefore, the nail | claw parts 65 and 76 comprise the temporary fixing part in this embodiment.

  The temporary fixing structure of the tank member 50, the plate member 60, and the intermediate layer material 70 will be described with reference to FIG. FIG. 16 is a vertical cross-sectional view in the longitudinal direction of the header tank 40 where the temporary fixing hole 54 and the claw portions 65 and 76 are formed.

  As shown in FIG. 16, in the present embodiment, the claw portions 65 and 76 are passed through the temporary fixing holes 54, bent along the outer periphery of the tank member 50, and caulked to be temporarily fixed. According to the evaporator 2 of the present embodiment, the same effect as that of the ninth embodiment can be obtained, and the tank member 50, the plate member 60, and the intermediate layer material 70 can be joined in a temporarily fixed state. The productivity of the evaporator (evaporator) can be improved.

  The temporary fixing hole and the temporary fixing claw portion are not limited to the combination of the present embodiment, and at least one of the tank member 50, the plate member 60, and the intermediate layer material 70 has another configuration. If temporarily fixed to at least one of the members, the same effect as in the present embodiment can be obtained.

(Other embodiments)
The present invention is not limited to the above-described embodiment, and can be variously modified as follows.

  (1) In the above-described embodiment, the example in which the flow part 51 of the tank member 50 and the connection part 62 of the plate member 60 are the bulging parts has been described, but the bulging part is not limited to the above example. For example, even if a burring hole with a flange for connecting a tube or the like has a sagging shape at the skirt portion, it corresponds to a bulging portion. Therefore, the same effect as that of the above-described embodiment can be exhibited by forming a recess in which the skirt portion of the burring hole is recessed in the intermediate layer material.

  (2) In the above-described embodiment, the example in which the bulging portions 51 and 62 are formed by press molding has been described. However, the bulging portions 51 and 62 are not limited to those formed by press molding. For example, even if the circulation part 51 of the tank member 50 is formed by bending, a sagging shape is generated at the skirt portion, and therefore the present invention can be applied.

  (3) In the above-described embodiment, the example in which the heat exchanger (heat radiator, evaporator) of the present invention is applied to a vehicle air conditioner constituting a supercritical refrigeration cycle has been described. The present invention may be applied to a heat exchanger (condenser or evaporator) for an air conditioner that constitutes a heat exchanger (radiator) used for cooling a vehicle engine or the like. Of course, the present invention is not limited to a vehicle and may be applied to a heat exchanger for other uses.

It is a whole block diagram of the heat exchanger of 1st Embodiment. (A) is AA sectional drawing of FIG. 1 of the heat exchanger of 1st Embodiment, (b) is BB sectional drawing of FIG. 1 of the heat exchanger of 1st Embodiment. (A) is AA sectional drawing of the heat exchanger of 2nd Embodiment of FIG. 1, (b) is BB sectional drawing of FIG. 1 of the heat exchanger of 2nd Embodiment. It is longitudinal direction sectional drawing of the header tank of the heat exchanger of 3rd Embodiment. (A) is AA sectional drawing of FIG. 4, (b) is BB sectional drawing of FIG. It is AA sectional drawing of FIG. 1 of the heat exchanger of 4th Embodiment. (A) is A'-A 'sectional drawing of the heat exchanger of 5th Embodiment of FIG. 1, (b) is BB sectional drawing of FIG. 1 of the heat exchanger of 5th Embodiment. is there. (A) is AA sectional drawing of the heat exchanger of 6th Embodiment of FIG. 1, (b) is BB sectional drawing of FIG. 1 of the heat exchanger of 6th Embodiment. (A) is AA sectional drawing of FIG. 1 of the heat exchanger of 7th Embodiment, (b) is BB sectional drawing of FIG. 1 of the heat exchanger of 7th Embodiment. It is AA sectional drawing of FIG. 1 of the heat exchanger of 8th Embodiment. It is a whole heat exchanger lineblock diagram of a 9th embodiment. It is a disassembled perspective view of the header tank of the heat exchanger of 9th Embodiment. (A) is sectional drawing including the EE line of FIG. 12 of the heat exchanger of 9th Embodiment, (b) is the FF line of FIG. 12 of the heat exchanger of 9th Embodiment. FIG. It is sectional drawing containing the GG line of FIG. 12 of the heat exchanger of 9th Embodiment. It is sectional drawing of the header tank of the heat exchanger of 10th Embodiment. It is sectional drawing of the header tank of the heat exchanger of 11th Embodiment. It is a disassembled perspective view of the header tank of the heat exchanger of a prior art. (A) is a longitudinal cross-sectional view of the header tank of a prior art, (b) is the Y section enlarged view of (a).

Explanation of symbols

10 ... Tube, 40 ... Header tank, 60 ... Plate member, 50 ... Tank member,
70, 70a ... intermediate layer material, 51 ... distribution part, 62 ... connection part, 71 ... concave part, 72 ... communication hole,
74 ... Position restricting part, 52, 64 ... Temporary fixing part, 65, 76 ... Claw part, 43 ... Through hole,
75 ... Communication passage.

Claims (18)

A plurality of tubes (10) through which fluid passes;
Header tanks (40) disposed on both ends of the plurality of tubes (10),
The header tank (40) includes a plate member (60) to which the tube (10) is connected, a tank member (50) combined with the plate member (60), the tank member (50), and the plate member. Intermediate layer material (70, 70a) interposed between (60) and
At least one of the tank member (50) and the plate member (60) has a bulging portion (51, 62) that swells on the opposite side of the intermediate layer material (70, 70a) and through which the fluid flows. In the formed heat exchanger,
On the surface facing the bulging portion (51, 62) of the intermediate layer material (70, 70a), a concave portion (71, 71a, 72). The heat exchanger characterized by the above-mentioned. 2. The heat according to claim 1, wherein the bulging part is a circulation part (51) formed in the tank member (50) and allowing fluid to flow in a longitudinal direction of the header tank (40). Exchanger. 3. The heat exchange according to claim 2, wherein the flow part (51) is formed close to any one end side in the width direction perpendicular to the longitudinal direction of the tank member (50). vessel. The heat exchanger according to claim 2 or 3, wherein a plurality of the flow sections (51) are provided along a longitudinal direction of the tank member (50). The depth dimension (H) of the flow part (51) relative to the flow part (51) formation surface of the tank member (50) is the width dimension of the flow part (51) on the flow part (51) formation surface ( The heat exchanger according to any one of claims 2 to 4, wherein the heat exchanger has a value equal to or greater than W). The said bulging part is a connection part (62) which is formed in the said plate member (60) and to which the said tube (10) is connected, The one of Claim 1 thru | or 5 characterized by the above-mentioned. Heat exchanger. 7. The intermediate layer material (70) is provided with a communication hole (72) for communicating the inside of the tube (10) and the tank member (50) side. The heat exchanger as described in any one. The said intermediate | middle layer material (70) is provided with the position control part (74) which controls the connection position of the said tube (10), The one of Claim 1 thru | or 7 characterized by the above-mentioned. Heat exchanger. The said intermediate | middle layer material (70) is comprised by the separate member separate from the said tank member (50) and the said plate member (60), It is any one of Claim 1 thru | or 8 characterized by the above-mentioned. The described heat exchanger. The heat exchanger according to claim 9, wherein the intermediate layer material (70) is formed of a bare material on which a brazing material is not clad. The heat exchanger according to claim 9 or 10, wherein the intermediate layer material (70) is formed by press molding. The heat exchanger according to claim 9 or 10, wherein the intermediate layer material (70) is formed by extrusion molding. The at least one constituent member among the tank member (50), the plate member (60), and the intermediate layer member (70) is temporarily fixed to at least one of the other constituent members (52). 64, 65, 76). A heat exchanger according to any one of claims 9 to 12, characterized in that it is provided. The said intermediate | middle layer material (70a) is comprised by bending at least one predetermined site | part of the said tank member (50) and the said plate member (60). The heat exchanger as described in any one. The plurality of tubes (10) are arranged in a stacked manner along the longitudinal direction of the header tank (40),
The heat exchanger according to any one of claims 1 to 14, wherein a plurality of rows in which the plurality of tubes (10) are arranged in a stack are provided. The said header tank (40) is provided with the through-hole (43) which penetrates the said tank member (50), the said plate member (60), and the said intermediate | middle layer material (70). 15. A heat exchanger according to 15. The said intermediate | middle layer material (70) is provided with the communicating path (75) which connects the said tubes (10) laminated | stacked and arrange | positioned at a different row | line | column, Either of Claim 15 or 16 characterized by the above-mentioned. The heat exchanger described in 1. The heat exchanger according to any one of claims 1 to 17, wherein the fluid is carbon dioxide.

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