JP2008101886A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger more rationally constituted. <P>SOLUTION: In this heat exchanger comprising cores 200a, 200b constituted by alternately stacking tubes 210 and fins 220, and tanks 300a, 300b, 300c, 300d provided with hole portions 311 for inserting end portions of the tubes, the tanks have the tubular shape long in the stacking direction of the tubes and fins, and respectively comprise a first hollow portion 321 communicated with the tube, a second hollow portion 322 communicated with a refrigerant inlet portion or outlet portion 301, 302, 303, and a wall portion 330 disposed between the first hollow portion and the second hollow portion, the wall portion has an opening portion 331 communicating the first hollow portion and the second hollow portion, the first hollow portion, the wall portion and the second hollow portion are successively positioned from a core side in a cross-section of the tank at a right angle to the stacking direction, and a diameter L2 in the direction orthogonal to the ventilating direction is larger than a diameter L1 in the ventilating direction. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention includes a core formed by alternately stacking tubes and fins, and a tank provided with a hole for inserting an end of the tube, and the core is ventilated and transmitted to the core. The present invention relates to a heat exchanger that performs heat exchange of a refrigerant flowing through the tube by heat.

  As heat exchangers such as radiators and evaporators used in the refrigeration cycle, a plurality of flat tubes and a plurality of corrugated fins are alternately laminated to form a core, and the end of the tube is formed into a pipe shape. What is inserted in a tank is known. The flat surface of the tube is configured to be parallel to the ventilation direction. The refrigerant is taken into the inside from the tank, circulates through the tube while exchanging heat by heat transmitted to the core, and then discharged from the tank to the outside.

  In addition, as a refrigerant for the refrigeration cycle, chlorofluorocarbon refrigerants, including alternative chlorofluorocarbons, have been widely adopted so far, but in recent years, there is a tendency to change this to CO2 in consideration of the global environment.

The refrigeration cycle using CO2 as a refrigerant has an extremely high internal pressure compared to a refrigeration cycle using a fluorocarbon refrigerant, and the pressure on the high pressure side in particular exceeds the critical point of the refrigerant depending on the use conditions such as the temperature. It is. The critical point is a limit on the high-pressure side (that is, a limit on the high-temperature side) where the gas layer and the liquid layer coexist, and is an end point on one side of the vapor pressure curve. The pressure, temperature, and density at the critical point are the critical pressure, critical temperature, and critical density, respectively. In particular, in a radiator that is a high-temperature heat source part of the refrigeration cycle, the refrigerant does not condense when the pressure exceeds the critical point of the refrigerant. For example, Patent Document 1 discloses an excellent heat exchanger that can be suitably used as a heat radiator for such a supercritical refrigeration cycle.
International Publication No. 2003/040640 Pamphlet

  Now, with regard to the heat exchanger of the refrigeration cycle, improvement of heat exchange efficiency of the refrigerant, reduction in size, weight reduction, ease of manufacture, and saving of installation space are important issues. In particular, a supercritical refrigeration cycle in which the pressure on the high pressure side exceeds the critical point of the refrigerant requires a very high pressure resistance compared to a refrigeration cycle that uses a fluorocarbon refrigerant. There is a need for further rationalization as well as ensuring safety.

  For example, in a heat exchanger for a supercritical refrigeration cycle, it is necessary to reduce the volume of tubes and tanks and to increase the wall thickness in terms of ensuring pressure resistance. Here, when the volume of the tank is small, the refrigerant is likely to be subjected to passage resistance, so that the pressure disparity inside the tank is increased, and there is a disadvantage that the flow rate of the refrigerant is greatly different for each tube. If the flow rate of the refrigerant is greatly different for each tube, the heat exchange efficiency is lowered. That is, in the heat exchanger manufacturing site, a configuration for equalizing the flow rate of the refrigerant in each tube is required while ensuring the pressure resistance of the tank.

  This invention is made | formed in view of this situation, The objective is to provide the heat exchanger comprised more rationally.

  The invention described in claim 1 of the present application includes a core formed by alternately stacking tubes and fins, and a tank provided with a hole portion into which an end of the tube is inserted. In the heat exchanger for exchanging heat of the refrigerant flowing through the tube with heat transmitted to the core, the tank is a tubular thing that is long in the stacking direction of the tube and the fin, and the tube A first hollow portion that communicates, a second hollow portion that communicates with an inlet portion or an outlet portion of the refrigerant, and a wall portion provided between the first hollow portion and the second hollow portion, The wall portion is provided with an opening for communicating the first hollow portion and the second hollow portion, and in the cross section of the tank perpendicular to the stacking direction, the first hollow is sequentially formed from the core side. Part, the wall part, and the second hollow part And, and, a heat exchanger in the radial direction is large structure perpendicular to the airflow direction than the diameter of the ventilation direction.

  With this configuration, even when the tank volume is small, the pressure disparity inside the tank can be kept small, and the flow rate of the refrigerant can be made uniform. Moreover, it can contribute to the saving of installation space.

  The invention described in claim 2 of the present application is the tube according to claim 1, wherein the tube has a flat shape, and the flat surface of the tube in the core is parallel to the ventilation direction. The said tube is a heat exchanger of the structure by which the width direction of the edge part was twisted by 90 degrees with respect to the said ventilation direction.

  With this configuration, the cross-sectional shape of the tank portion with respect to the ventilation direction can be further reduced, which can contribute to saving installation space.

  The invention described in claim 3 of the present application is the tank according to claim 1 or 2, wherein the tank is formed by integrally forming the first tank member provided with the hole, the second hollow portion, and the wall portion. It is a heat exchanger configured to join two tank members.

  With this configuration, the manufacture of the tank portion can be facilitated.

  According to a fourth aspect of the present invention, in the first or second aspect of the present invention, the tank includes a tank body member formed integrally with the first hollow portion and the second hollow portion, and a wall constituting the wall portion. It is a heat exchanger of the structure formed by joining a part component member.

  With this configuration, the manufacture of the tank portion can be facilitated.

  According to a fifth aspect of the present invention, in any one of the first to fourth aspects, the wall portion is provided with the plurality of openings, and the plurality of openings has a flow rate of the refrigerant in each tube. The heat exchanger has a configuration in which the areas or intervals thereof are made different depending on the position of the inlet portion or the outlet portion so as to be uniform.

  With this configuration, if the flow rate of the refrigerant in each tube is made uniform, the heat exchange efficiency of the refrigerant can be reliably improved.

  The invention described in claim 6 of the present application is the heat exchanger according to any one of claims 1 to 5, wherein the heat exchanger is configured by stacking a plurality of the cores in the ventilation direction.

  With this configuration, the heat exchange efficiency of the refrigerant can be improved.

  The invention described in claim 7 of the present application is the invention according to claim 6, comprising a plurality of tanks respectively provided in the plurality of cores and arranged in the ventilation direction, wherein the width of the plurality of cores with respect to the ventilation direction is set. When the width of the plurality of tanks with respect to LC and the ventilation direction is LT, they are heat exchangers having a configuration in which LC ≧ LT.

  With this configuration, it is possible to contribute to the saving of installation space in the installation of the heat exchanger that improves the heat exchange efficiency of the refrigerant in the vehicle.

  The invention described in claim 8 of the present application is that in claim 6 or 7, the core includes a first core and a second core stacked in the ventilation direction, and the tank includes the first core of the first core. A first tank into which one end of the tube is inserted; a second tank into which the other end of the first core tube is inserted; and a third tank into which one end of the second core tube is inserted. And a fourth tank into which the other end of the tube of the second core is inserted, wherein the first tank is provided with the refrigerant inlet, and the second tank is provided with the refrigerant outlet. The third tank is provided with an inlet for the refrigerant, the fourth tank is provided with an outlet for the refrigerant, the outlet of the second tank and the inlet of the third tank are communicated, One core is leeward in the ventilation direction, and the second core is the ventilation method A heat exchanger configured to place the upwind.

  With this configuration, since the first core and the second core can be manufactured in the same configuration and then stacked in the ventilation direction, the manufacturing method can be facilitated.

  The invention described in claim 9 of the present application is that in claim 6 or 7, the core includes a first core and a second core stacked in the ventilation direction, and the tube has a flow direction of the refrigerant. The refrigerant having a U-turn part to be reversed and circulating through the first core is reversed at the U-turn part and flows through the second core, and the tank is the tube on the first core side. One tank into which the end of the tube is inserted and the other tank into which the end of the tube on the second core side is inserted. The one tank is provided with an inlet for the refrigerant, and the other tank Is a heat exchanger having a configuration in which an outlet portion of the refrigerant is provided, the first core is arranged leeward in the ventilation direction, and the second core is arranged upwind in the ventilation direction.

  With this configuration, the manufacturing method can be facilitated by reducing the number of parts and simplifying the assembly process. Moreover, weight reduction can be achieved by reducing the number of components.

  The invention described in claim 10 of the present application is the heat exchanger according to any one of claims 1 to 9, wherein the heat exchanger is used in a refrigeration cycle in which the refrigerant is circulated, and the refrigeration cycle has a high pressure side pressure. Is a heat exchanger having a configuration exceeding the critical point of the refrigerant.

  That is, the heat exchanger of the present invention can be used very suitably as a supercritical refrigeration cycle.

  According to the present invention, a more rationally configured heat exchanger can be obtained.

  Embodiments of the present invention will be described below with reference to FIGS. A refrigeration cycle 1 shown in FIG. 1 is for in-vehicle air conditioning installed in an automobile. The compressor 2 compresses the refrigerant, the radiator 100 cools the refrigerant compressed by the compressor 2, and is cooled by the radiator 100. The expansion valve 3 that expands by decompressing the generated refrigerant, the evaporator 4 that evaporates the refrigerant depressurized by the expansion valve 3, the refrigerant that flows out of the evaporator 4 is separated into an air layer and a liquid layer, and the refrigerant in the gas layer is An accumulator 5 to be sent to the compressor 2 and an internal heat exchanger 6 that improves the efficiency of the refrigeration cycle 1 by exchanging heat between the high-pressure side refrigerant and the low-pressure side refrigerant are provided. CO2 is used as the refrigerant, and the pressure on the high pressure side of the supercritical refrigeration cycle 1 exceeds the critical point of the refrigerant depending on the use conditions such as the temperature. The arrows in the figure indicate the direction of refrigerant circulation.

  As shown in FIGS. 2 and 3, the radiator 100 as the heat exchanger of the present example includes a plurality of alternately laminated flat tubes 210 through which a refrigerant flows and corrugated fins 220 provided with louvers. Cores 200a, 200b and a plurality of tanks 300a, 300b, 300c, 300d provided with holes 311 for inserting and connecting the ends of the tubes 210, and venting the cores 200a, 200b. In addition, the heat exchange of the refrigerant flowing through the tube 210 is performed by heat transmitted to the cores 200a and 200b.

  The radiator 100 is formed by stacking a plurality of cores 200a and 200b in the ventilation direction. That is, the core includes a first core 200a and a second core 200b that are stacked in the ventilation direction. Further, as the tank, a first tank 300a into which one end 211 of the tube 210 of the first core 200a is inserted, a second tank 300b into which the other end 211 of the tube 210 of the first core 200a is inserted, A third tank 300c into which one end 211 of the tube 210 of the second core 200b is inserted, and a fourth tank 300d into which the other end 211 of the tube 210 of the second core 200b is inserted. The first tank 300a and the fourth tank 300d are arranged in the ventilation direction. Similarly, the second tank 300b and the third tank 300c are also arranged in the ventilation direction.

  Each of the tanks 300a, 300b, 300c, and 300d has a tubular shape that is long in the stacking direction of the tubes 210 and the fins 220, and a plurality of holes 311 are arranged along the stacking direction. Further, both end portions in the stacking direction are closed by a closing member 312 having a predetermined shape.

  The first tank 300a is provided with a refrigerant inlet 301, the second tank 300b and the third tank 300c are provided with a communication pipe 302 that communicates them, and the fourth tank 300d is provided with a refrigerant outlet 303. . The communication pipe 302 is a refrigerant outlet for the second tank 300b and a refrigerant inlet for the third tank. The refrigerant sent from the compressor 2 flows in from the inlet portion 301 of the first tank 300a, and the refrigerant flowing out from the outlet portion 303 of the fourth tank 300d is sent to the expansion valve 3.

  In the case of this example, the first core 200a is disposed leeward in the ventilation direction, and the second core 200b is disposed leeward in the ventilation direction. That is, the heat exchange efficiency is improved by using a so-called counterflow for the refrigerant. The arrows in FIGS. 2 and 3 indicate the flow direction of the refrigerant in the radiator 100, and the white arrows indicate the ventilation direction with respect to the first core 200a and the second core 200b.

  As shown in FIGS. 4 and 5, in the tube 210 of this example, the width direction of both end portions 211 is twisted by 90 ° with respect to the ventilation direction. The flat surface of the tube 210 in each of the cores 200a and 200b is parallel to the ventilation direction.

  The tube 210 is an extruded tube made of an aluminum alloy. A plurality of flow paths 212 are arranged in the width direction. The end portion 211 of the tube 210 is plastically deformed by cutting the extruded tube into a predetermined length, sandwiching the end portion 211 and the vicinity thereof with a pair of jigs, and moving each jig relative to each other. Yes.

  The heat radiator 100 includes a tube 210, fins 220, a first tank 300a, a second tank 300b, a third tank 300c, and a member that constitutes the fourth tank 300d, and then the assembly is placed in the furnace. It is manufactured by brazing. At the time of such brazing, a brazing material and a flux are provided in advance at the main points of each member.

  Next, each tank 300a, 300b, 300c, 300d of this example will be described in detail. As shown in FIGS. 6 to 9, the first tank 300a of this example includes a first hollow portion 321 that communicates with the tube 210, a second hollow portion 322 that communicates with the refrigerant inlet portion 301, and a first hollow portion. 321 and the second hollow portion 322 are provided with a wall portion 330. The wall portion 330 is provided with an opening 331 that allows the first hollow portion 321 and the second hollow portion 322 to communicate with each other. The openings 331 are provided at predetermined intervals in the stacking direction of the tubes 210 and the fins 220.

  In the case of this example, in the cross section of the first tank 300a that is perpendicular to the stacking direction of the tubes 210 and the fins 220, the first hollow portion 321, the wall portion 330, and the second hollow portion 322 are positioned in order from the core 200 side. In addition, the diameter L2 in the direction orthogonal to the ventilation direction is set larger than the diameter L1 in the ventilation direction (see FIG. 6).

  In addition, the first tank 300a joins a first tank member 341 provided with a hole 311 for connecting the tube 210 and a second tank member 342 formed integrally with the second hollow portion 322 and the wall portion 330. It will be. The first tank member 341 is a member having a U-shaped cross section, and is configured such that the inner side thereof becomes the first hollow portion 321 by joining both ends of the U shape to the second tank member 342. The illustrated second tank member 342 has a shape that fits both ends of the U-shape. The first tank member 341 is formed by subjecting an extrusion member or an aluminum alloy flat plate to a predetermined process. The second tank member 342 is formed by subjecting the extruded member to predetermined processing.

  The basic configuration of the second tank 300b, the third tank 300c, and the fourth tank 300d is the same as that of the first tank 300a, and is not shown. A connection hole 350 for connecting the inlet portion 301, the communication pipe 302, or the outlet portion 303 is provided at a main point of the second tank member 342 of each of the tanks 300 a, 300 b, 300 c, and 300 d.

  According to the first tank 300 a and the third tank 300 c, the refrigerant flows into the second hollow portion 322 from the inlet portion 301 or the communication pipe 302, passes through the opening portion 331 of the wall portion 330, and passes through the second hollow portion 322. 1 flows into the hollow portion 321 and is distributed from the first hollow portion 321 to each tube 210.

  According to the second tank 300b and the fourth tank 300d, the refrigerant flows into the first hollow portion 321 from each tube 210, passes through the opening 331 of the wall portion 330, and passes from the first hollow portion 321 to the second hollow portion 322. To the outlet portion 303 or the communication pipe 302 from the second hollow portion 322.

  According to such a configuration, the pressure resistance and the heat exchange efficiency of the refrigerant can be reliably improved. That is, since the refrigerant is configured to pass through the opening 331 of the wall 330, the pressure disparity inside each of the tanks 300a, 300b, 300c, and 300d is alleviated, and the flow rate of the refrigerant in each tube 210 is equalized. . As a result, the heat exchange efficiency is improved. Furthermore, according to the wall part 330, the mechanical strength of each tank 300a, 300b, 300c, 300d is ensured, and pressure resistance is improved. Usually, in view of the pressure resistance of the tank, it is desirable that the cross-sectional shape is circular. However, according to such a wall portion 330, L2 can be set longer than L1, and the volume of the entire tank can be set. Can be increased. Such an advantage is very effective in improving the degree of design freedom in the radiator 100 of the supercritical refrigeration cycle that requires excellent pressure resistance. In this example, the first tank 300a and the fourth tank 300d, and the second tank 300b and the third tank 300c are provided before and after the ventilation direction, but since L1 is set relatively short, The dimensions of the tanks 300a, 300b, 300c, and 300d are balanced with respect to the widths of the first core 200a and the second core 200b.

  As described above, the heat exchanger of this example has a streamlined structure in consideration of improving the heat exchange efficiency of the refrigerant, downsizing, reducing weight, facilitating manufacturing, and saving installation space. Therefore, it can be used very suitably as a radiator of a supercritical refrigeration cycle mounted on an automobile. It should be noted that the configuration of each part in this example can be appropriately changed in design within the technical scope described in the claims, and is of course not limited to that described above.

  For example, as shown in FIG. 10, the position of the connection hole 350 can be set as appropriate. Further, the flow rate of the refrigerant in each tube 210 tends to increase as it approaches the inlet portion 301 or the outlet portion 303. Therefore, the plurality of openings 331 provided in the wall 330 may have different areas or intervals depending on the position of the inlet portion 301 or the outlet portion 303 so that the flow rate of the refrigerant in each tube 210 is uniform. . In the illustrated example, the area of each opening 331 is set so as to gradually increase as the distance from the connection hole 350 connecting the inlet portion 301 or the outlet portion 303 increases. Or the area of each opening part 331 may be made the same, and you may make it set the space | interval gradually as they leave | separate from the connection hole 350. FIG. Thus, if the area and interval of the opening 331 are set and the flow rate of the refrigerant in each tube 210 is made uniform, the heat exchange efficiency of the refrigerant can be further improved.

  Further, as shown in FIGS. 11 and 12, each of the tanks 300a, 300b, 300c, and 300d is constituted by joining a plate-like first tank member 341 and a second tank member 342 having a shape for holding the same. It is also possible to do. The shapes of the first tank member 341 and the second tank member 342 may be appropriately set to facilitate the processing thereof.

  Alternatively, as shown in FIGS. 13 and 14, each of the tanks 300 a, 300 b, 300 c, and 300 d includes a tank body member 361 in which the first hollow portion and the second hollow portion are integrally formed, and a wall portion 330. It is also possible to configure by joining the wall constituting member 362 to be joined.

  Further, as shown in FIG. 15, the width of the plurality of cores 200a and 200b in the ventilation direction is LC, the width of the first tank 300a and the fourth tank 300d in the ventilation direction, or the width of the second tank 300b and the third tank 300c. When the width is LT, they should be set so that the relationship LC ≧ LT is satisfied. In the example shown in the figure, the width occupied by the plurality of tubes 210 is LC. However, when the fin 220 protrudes beyond this, the width including the width occupied by the fin 220 is LC. If the dimensions of the respective parts are set in this way, it is possible to further contribute to the saving of installation space in installation on a vehicle. That is, according to this example, since the diameter L1 in the ventilation direction of each tank 300a, 300b, 300c, 300d is smaller than the diameter L2 in the direction orthogonal to the ventilation direction, the volume of each tank 300a, 300b, 300c, 300d is sufficient. The LT can be set small while ensuring the same. Therefore, the dimensions of the cores 200a, 200b and the tanks 300a, 300b, 300c, 300d can be set with a good balance.

  Next, another embodiment of the present invention will be described with reference to FIGS. The heat exchanger 1 of this example shown in these drawings uses a tube 210 provided with a U-turn portion 213 that reverses the direction in which the refrigerant flows. The refrigerant that has circulated through the first core 200a is inverted at the U-turn portion 213 and circulates through the second core 200b. The tank includes one tank 300a into which the end portion 211 of the tube 210 on the first core 200a side is inserted and the other tank 300d into which the end portion 211 of the tube 210 on the second core 200b side is inserted. One tank 300a is provided with a refrigerant inlet 301, and the other tank 300d is provided with a refrigerant outlet 303. One tank 300a corresponds to the first tank of the above-described embodiment, and the other tank 300d corresponds to the fourth tank of the above-described embodiment. That is, by adopting the tube 210 having the U-turn part 213, the second tank 300b and the third tank 300c in the above-described embodiment are omitted. Other configurations are the same as those in the above-described embodiment, and common members are denoted by the same reference numerals and description thereof is omitted.

  As described above, the tube 210 may be provided with the U-turn portion 213 so that the tube of the first core 200a and the tube of the second core 200b can be integrated. According to the configuration of this example, the number of tanks can be reduced, and further reduction in installation space and improvement in manufacturability can be achieved.

  The heat exchanger of the present invention can be used very suitably as a radiator of a supercritical refrigeration cycle.

It is explanatory drawing which concerns on the Example of this invention and shows a supercritical refrigerating cycle. It is a front view which concerns on the Example of this invention and shows a heat exchanger. It is an upper surface sectional view showing a heat exchanger concerning an example of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS It is related with the Example of this invention, (a) is a top view which shows a tube, (b) is a front view which shows a tube. It is a sectional view showing a tube concerning an example of the present invention. It is an upper surface sectional view showing an important section of a heat exchanger concerning an example of the present invention. It is an upper surface exploded sectional view showing a tank concerning an example of the present invention. (A) is the front view which shows the 1st tank member, (b) is the top view, (c) is the side view, (d) is the back view concerning the Example of this invention. (A) is the front view which shows the 2nd tank member, (b) is the top view, (c) is the side view, (d) is the back view concerning the Example of this invention. (A) is the front view which shows the 2nd tank member, (b) is the top view, (c) is the side view, (d) is the back view concerning the Example of this invention. It is an upper surface sectional view showing an important section of a heat exchanger concerning an example of the present invention. It is an upper surface exploded sectional view showing a tank concerning an example of the present invention. It is an upper surface sectional view which shows the principal part of the heat exchanger according to the embodiment of the present invention and according to the embodiment of the present invention. It is an upper surface exploded sectional view showing a tank concerning an example of the present invention. It is an upper surface sectional view showing an important section of a heat exchanger concerning an example of the present invention. It is a front view which concerns on the Example of this invention and shows a heat exchanger. It is an upper surface sectional view showing a heat exchanger concerning an example of the present invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Supercritical refrigeration cycle 2 Compressor 3 Expansion valve 4 Evaporator 5 Accumulator 6 Internal heat exchanger 100 Radiator 200a 1st core 200b 2nd core 210 Tube 211 End part 212 Flow path 213 U-turn part 220 Fin 300a 1st tank 300b 1st 2 tank 300c 3rd tank 300d 4th tank 301 Inlet part 302 Communication pipe 303 Outlet part 311 Hole part 312 Closing member 321 1st hollow part 322 2nd hollow part 330 Wall part 331 Opening part 341 1st tank member 342 2nd tank Member 350 Connection hole 361 Tank body member 362 Wall component member

Claims (10)

It comprises a core formed by alternately stacking tubes and fins, and a tank provided with a hole for inserting an end of the tube, and is ventilated through the core, and heat transmitted to the core In the heat exchanger that performs heat exchange of the refrigerant flowing through the tube,
The tank has a tubular shape that is long in the stacking direction of the tube and the fin, and includes a first hollow portion that communicates with the tube, a second hollow portion that communicates with an inlet portion or an outlet portion of the refrigerant, and the first A wall provided between one hollow part and the second hollow part,
The wall portion is provided with an opening communicating the first hollow portion and the second hollow portion,
In the cross section of the tank perpendicular to the stacking direction, the first hollow portion, the wall portion, and the second hollow portion are located in order from the core side, and the diameter is larger than the diameter in the ventilation direction. A heat exchanger having a large diameter in a direction orthogonal to the ventilation direction. The tube is flat,
The flat surface of the tube in the core is parallel to the ventilation direction,
The heat exchanger according to claim 1, wherein the tube has a width direction at an end thereof twisted at 90 ° with respect to the ventilation direction.   2. The tank according to claim 1, wherein the tank is formed by joining the first tank member provided with the hole and the second tank member formed integrally with the second hollow portion and the wall portion. 2. The heat exchanger according to 2.   2. The tank according to claim 1, wherein the tank is formed by joining a tank body member formed integrally with the first hollow portion and the second hollow portion and a wall portion constituting member of the wall portion. 2. The heat exchanger according to 2. The wall is provided with a plurality of openings.
The plurality of openings have different areas or intervals according to the position of the inlet or outlet so that the flow rate of the refrigerant in each tube is uniform. The heat exchanger in any one of thru | or 4.   The heat exchanger according to any one of claims 1 to 5, wherein the heat exchanger is formed by stacking a plurality of the cores in the ventilation direction.   A plurality of the tanks respectively provided in the plurality of cores and arranged in the ventilation direction are provided, LC is a width of the plurality of cores with respect to the ventilation direction, and LT is a width of the plurality of tanks with respect to the ventilation direction. The heat exchanger according to claim 6, wherein they are in a relationship of LC ≧ LT. The core includes a first core and a second core stacked in the ventilation direction,
The tank includes a first tank into which one end of the first core tube is inserted, a second tank into which the other end of the first core tube is inserted, and a tube of the second core. A third tank for inserting one end, and a fourth tank for inserting the other end of the tube of the second core,
The first tank is provided with the refrigerant inlet, the second tank is provided with the refrigerant outlet, the third tank is provided with the refrigerant inlet, and the fourth tank is provided with the refrigerant. The outlet portion of the second tank and the inlet portion of the third tank are communicated,
The heat exchanger according to claim 6 or 7, wherein the first core is disposed leeward in the ventilation direction, and the second core is disposed upstream of the ventilation direction. The core includes a first core and a second core stacked in the ventilation direction,
The tube includes a U-turn portion that reverses the flow direction of the refrigerant, and the refrigerant that has flowed through the first core is reversed at the U-turn portion and flows through the second core,
The tank includes one tank for inserting the end of the tube on the first core side, and the other tank for inserting the end of the tube on the second core side,
The one tank is provided with the refrigerant inlet, the other tank is provided with the refrigerant outlet,
The heat exchanger according to claim 6 or 7, wherein the first core is disposed leeward in the ventilation direction, and the second core is disposed upstream of the ventilation direction.   The said heat exchanger is used for the refrigerating cycle which circulates the said refrigerant | coolant, and the said refrigerating cycle has the pressure of the high voltage | pressure side exceeding the critical point of the said refrigerant | coolant, The any one of the Claims 1 thru | or 9 characterized by the above-mentioned. The described heat exchanger.

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