JP2005127611A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger capable of reducing the number of components and improving its assembling workability. <P>SOLUTION: This heat exchanger 1 performs the heat exchange between a refrigerant of high temperature and high pressure and a refrigerant of low temperature and low pressure, and has a strip sheet-shaped tube 2 wherein a high-pressure side refrigerant flow channel 6 where the refrigerant of high temperature and high pressure flows and a low-pressure side refrigerant flow channel 8 where the refrigerant of low temperature and low pressure flows, are integrally formed, and headers 4a, 4b mounted on both ends of the strip sheet-shaped tube member and fixed by inserting the strip sheet-shaped tube from tube insertion grooves 14a, 14b. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a heat exchanger, and more particularly to a heat exchanger used for an intercooler of a vehicle air conditioner in a supercritical refrigeration cycle using carbon dioxide or the like as a refrigerant.

Conventionally, when a refrigerant having a low critical point such as carbon dioxide is used in a refrigerant circuit of a vehicle air conditioner, in order to increase the heat dissipation capability and refrigerant capability of the radiator, An intercooler as described in Document 1 is provided.
A conventional heat exchanger used for the intercooler and the like will be specifically described with reference to FIGS. FIG. 5 is an exploded perspective view showing a conventional heat exchanger. 6 is a cross-sectional view taken along the line CC in the conventional heat exchanger shown in FIG. FIG. 7 is a DD cross-sectional view of the strip tube portion of the conventional heat exchanger shown in FIG.
As shown in FIGS. 5 to 7, a conventional heat exchanger 50 includes a belt-like high-pressure strip tube 52 having a refrigerant passage 51 through which a high-temperature and high-pressure refrigerant flows, and a refrigerant passage 53 through which a low-temperature and low-pressure refrigerant flows. And a belt-like low-pressure strip plate tube 54.
The high pressure strip tube 52 is provided with a plurality of holes 52a (see FIG. 7), and the plurality of holes 52a form a refrigerant flow path through which the high-temperature and high-pressure refrigerant flows. On the other hand, the low-pressure strip plate tube 54 is also provided with a plurality of holes 54a (see FIG. 7), and the plurality of holes 54a form a refrigerant flow path through which the low-temperature and low-pressure refrigerant flows. In order to reduce the pressure loss of the circulating refrigerant, the refrigerant passage formed in the low-temperature strip plate tube 54 has a cross-sectional area of the hole 54a, which is a cross section of the flow path, in the flow path of the refrigerant flow path through which the high-temperature and high-pressure refrigerant flows. It is larger than the road cross-sectional area.
Both ends of the high-pressure strip tube 52 are respectively fitted into the grooves 56a of the high-pressure header 56 and brazed, and both ends of the low-pressure strip tube 54 are respectively fitted into the grooves 58a of the low-pressure header 58 and brazed. Has been. Further, the high-pressure strip tube 52 and the low-pressure strip tube 54 are laminated so as to be overlapped with each other, and the planes are brazed.

JP 2002-340485 A (page 4-8, FIGS. 1 to 5)

However, in the conventional heat exchanger 50, the brazing area in parts such as the high-pressure strip tube 52 and the low-pressure strip tube 54 is large, and there is a possibility that the defective rate of the brazed portion is high. There is a problem that the functionality is likely to be impaired.
Further, the conventional heat exchanger 50 has a problem that the number of parts is large and the assemblability is poor, so that the manufacturing cost is increased.
Further, the conventional heat exchanger 50 has a problem that it is difficult to position the tubes in the headers when the tubes 52 and 54 are inserted into the headers 56 and 58, respectively.

Accordingly, the present invention has been made to solve the above-described problems of the prior art, and an object of the present invention is to provide a heat exchanger that can reduce the number of parts and improve the assemblability.
It is another object of the present invention to provide a heat exchanger that can reduce the brazing location and area of components and reduce the defect rate.
Furthermore, an object of the present invention is to provide a heat exchanger that can easily position a tube that forms a refrigerant flow path in a header.
Another object of the present invention is to provide a heat exchanger capable of reducing the pressure loss of the refrigerant flowing in the tube forming the refrigerant flow path.
Furthermore, the present invention forms a refrigeration cycle by using a supercritical fluid as a refrigerant, a compressor that compresses the refrigerant, a radiator, an evaporator, and a depressurizing unit, and the heat exchanger described above includes a radiator and a depressurizing unit. It is an object of the present invention to provide a vapor compression supercritical refrigeration cycle apparatus using an internal heat exchanger that exchanges heat between the refrigerant between the refrigerant and the refrigerant sucked into the compressor.
Another object of the present invention is to provide a vehicle air conditioner using the above-described vapor compression supercritical refrigeration cycle apparatus.

In order to achieve the above object, a first invention of the present invention is a heat exchanger for exchanging heat between a high-temperature and high-pressure refrigerant and a low-temperature and low-pressure refrigerant, and the high-pressure side through which the high-temperature and high-pressure refrigerant flows. A strip plate-like tube member integrally formed with a refrigerant channel and a low-pressure side refrigerant channel through which a low-temperature and low-pressure refrigerant flows, and the strip plate-like tube provided at both ends of the strip plate-like tube member from the tube insertion groove And a header member into which the member is inserted and fixed.
In the present invention configured as described above, since the plurality of high-pressure side refrigerant flow paths and the plurality of low-pressure side refrigerant flow paths are integrally provided in the strip-like tube member, the number of parts is reduced, and the related art The number of brazing points can be reduced as compared with the tube member, and the reliability in terms of the function of the heat exchanger can be improved. Furthermore, when attaching the edge part of a tube member to a header member, the edge part of a tube member can be easily positioned inside a header member, and assembly property can be improved.

In the first invention of the present invention, preferably, the strip-shaped tube member includes a plurality of high-pressure side refrigerant flow paths and a plurality of low-pressure side refrigerant flow paths.
In the first invention of the present invention, preferably, each of the high-pressure side refrigerant flow path and the low-pressure side refrigerant flow path of the strip plate tube member has a circular cross section.
In the first invention of the present invention, preferably, the cross section of the low-pressure side refrigerant flow path of the strip-shaped tube member is formed larger than the cross section of the high-pressure side refrigerant flow path. According to the first aspect of the invention, the flow rate of the refrigerant flowing in the low-pressure side refrigerant flow path can be reduced, and the pressure loss of the low-pressure side refrigerant can be reduced.
In the first invention of the present invention, preferably, the high-pressure side refrigerant flow paths and the low-pressure side refrigerant flow paths of the strip plate-like tube member are alternately arranged in a staggered manner.
According to the first aspect of the present invention thus configured, the wall thickness between the high-temperature side refrigerant flow path and the low-temperature side refrigerant flow path can be reduced, and the overall weight is reduced. Can be made.
In the first invention of the present invention, preferably, the strip plate-like tube member is inserted to the depth surface inside the header member, and the strip plate-like tube member allows the header member to be connected to the high-pressure side refrigerant flow path and the low-pressure side. It is comprised so that it may partition with a refrigerant flow path.
Also, in the first invention of the present invention, preferably, the header member is configured such that a tube guide groove is formed in an inner depth surface thereof, and an end portion of the strip plate-like tube member is received by the tube guide groove. Has been.
In the first invention of the present invention, preferably, the high-pressure side refrigerant flow path of the strip-shaped tube member and the high-pressure side refrigerant flow path of the header member are provided on the side surface of the portion inserted into the header member of the strip-shaped tube member. A high-pressure side communication channel that communicates, and a low-pressure side communication channel that connects the low-pressure side refrigerant channel of the strip-shaped tube member and the low-pressure side refrigerant channel of the header member are formed.
In the first invention of the present invention, preferably, the tube insertion groove of the strip-like tube member is formed closer to the high-pressure side refrigerant flow path than the header central portion.
In the first invention of the present invention, preferably, the belt-like tube member is formed by an extrusion process using an integral extrusion material, or is formed by a drawing process using an integral drawing material.
Furthermore, in the first invention of the present invention, preferably, the header member is formed by an extrusion process using an integral extrusion material, or is formed by a drawing process using an integral drawing material.

A second aspect of the present invention is a vapor compression supercritical refrigeration cycle apparatus that forms a refrigeration cycle using a supercritical fluid as a refrigerant, a compressor that compresses the refrigerant, a radiator, an evaporator, and a decompression unit. And an internal heat exchanger that exchanges heat between the high-pressure side refrigerant between the radiator and the decompression means and the low-pressure side refrigerant sucked into the compressor. The heat exchanger according to the first aspect is used.
The third aspect of the present invention is a vehicle air conditioner using the vapor compression supercritical refrigeration cycle apparatus of the second aspect of the present invention.

As described above, according to the heat exchanger of the first invention of the present invention, the number of parts can be reduced and the assemblability can be improved. Moreover, the location and area of brazing regarding related parts of the heat exchanger can be reduced, and the defect rate can be reduced. Furthermore, the tube forming the refrigerant flow path can be easily positioned on the header. Moreover, the pressure loss of the refrigerant flowing in the tube forming the refrigerant flow path can be reduced.
Moreover, according to the vapor compression supercritical refrigeration cycle apparatus of the second invention of the present invention and the vehicle air conditioner of the third invention of the present invention using this apparatus, an intercooler can be easily manufactured. Therefore, the manufacturing cost can be reduced.

Hereinafter, an embodiment of a heat exchanger of the present invention will be described with reference to the accompanying drawings.
FIG. 1 is an overall exploded perspective view showing a heat exchanger according to an embodiment of the present invention. 2 is a cross-sectional view taken along the line AA in the heat exchanger according to the embodiment of the present invention shown in FIG. FIG. 3 is a BB cross-sectional view of the strip-like tube portion of the heat exchanger according to the embodiment of the present invention shown in FIG. In addition, the arrow of the broken line in FIG.1 and FIG.2 has shown the flow direction of the refrigerant | coolant.
As shown in FIGS. 1 to 3, the heat exchanger 1 according to the embodiment of the present invention is coupled to a strip plate tube 2 in which heat exchange of refrigerant is performed, and both ends of the strip plate tube 2. A pair of headers 4a and 4b is provided.
The strip-like tube 2 is obtained by integrally forming a plurality of round holes 6 and 8 by extruding or drawing a metal piece made of aluminum or the like or a clad material. As shown in FIGS. 1 and 2, the plurality of round holes 6, 8 extend through the horizontal direction. Further, as shown in FIG. 3, the round holes 6 and the round holes 8 are arranged in a staggered manner in the vertical direction, and the round holes 6 are high-pressure side refrigerant passages that are refrigerant passages through which high-temperature and high-pressure refrigerant flows. Yes, the round hole 8 is a low-pressure side refrigerant flow path that is a refrigerant flow path through which the low-temperature low-pressure refrigerant flows.
Further, in order to reduce the pressure loss of the refrigerant flowing in the low-pressure side refrigerant flow path 8, the cross-sectional area of the round hole 8 is designed to be larger than the cross-sectional area of the round hole 6. Preferably, the ratio of the total cross-sectional area to the total cross-sectional area of the low-pressure side refrigerant flow path 8 is 1/3 or less.
Here, in the present embodiment, as described above, a mode in which the cross-sectional area of the round hole 8 is designed to be larger than the cross-sectional area of the round hole 6 is described as an example. The number of the low-pressure side refrigerant flow paths 8 is set so that the ratio of the total cross-sectional area of the high-pressure side refrigerant flow paths 6 to the total cross-sectional area of the low-pressure side refrigerant flow paths 8 is 1/3 or less. You may design so that it may increase more than the number of the paths 6. FIG.

Further, grooves 10a, 10b, 12a and 12b extending through the respective round holes 6 and 8 in the vertical direction are provided by milling or the like in portions adjacent to both end faces 2a and 2b of the strip plate tube 2. . The grooves 10a and 10b communicate with the round hole 6 (the high-pressure side refrigerant flow path 6) and function as a high-pressure side refrigerant flow path, and the high-temperature and high-pressure refrigerant that has flowed into the high-pressure side refrigerant flow path 10a flows into the high-pressure side refrigerant flow path inlet 6a. From the high pressure side refrigerant flow path 6b, and flows out from the high pressure side refrigerant flow path outlet 6b to the high pressure side refrigerant flow path 10b.
On the other hand, the grooves 12a and 12b communicate with the round hole 8 (low-pressure side refrigerant flow path 8) to function as a low-pressure side refrigerant flow path, and the low-temperature and low-pressure refrigerant flowing into the low-pressure side refrigerant flow path 12a It passes through the low pressure side refrigerant flow path 8 from the inlet 8a and flows out from the low pressure side refrigerant flow path outlet 8b to the low pressure side refrigerant flow path 12b.

Next, the headers 4a and 4b to which the strip plate tube 2 is connected are formed by extruding or drawing a metal piece or a clad material made of aluminum or the like, like the strip plate tube 2. is there.
Each header 4a, 4b is provided with strip plate-like tube insertion grooves 14a, 14b formed in conformity with the shape of the end faces 2a, 2b of the strip plate tube 2, and the strip plates are formed in the insertion grooves 14a, 14b. The end of the tube 2 can be inserted.
Further, the end faces 2a and 2b of the strip plate tube 2 inserted from the strip plate tube insertion grooves 14a and 14b are formed into strip plate tube guide grooves 16a and 16b provided in the depth surface inside the headers 4a and 4b. It is guided and inserted until it contacts the depth surface inside the header 4a, 4b. The end faces 2a and 2b of the strip-like tube 2 are brazed to the depth surfaces inside the headers 4a and 4b after contacting the depth surfaces inside the headers 4a and 4b. Here, the positions of the strip plate-like tube insertion grooves 14a and 14b and the strip plate-like tube guide grooves 16a and 16b in the headers 4a and 4b are located on the higher pressure side than the central portions of the headers 4a and 4b (FIG. 2). reference).

Further, in a state where the strip plate tube 2 and the headers 4a and 4b are joined by brazing, the grooves 10a and 10b (high pressure side refrigerant flow paths 10a and 10b) and the grooves 12a and 12b (low pressure side) of the strip plate tube 2 are combined. The refrigerant flow paths 12a, 12b) are positioned inside the headers 4a, 4b. Moreover, since these groove | channel 10a and groove | channel 12b and the groove | channel 10b and groove | channel 12a are partitioned off by the thickness 13a, 13b of the strip | belt-plate tube 2 provided between each other, the strip | belt-plate tube 2 is made into header 4a. , 4b and brazed, the refrigerant in the high-pressure side refrigerant flow paths 10a, 10b and the low-pressure side refrigerant flow paths 12a, 12b are partitioned.
Further, the high-pressure side refrigerant flow paths 10a and 10b of the strip-like tube 2 positioned inside the headers 4a and 4b are the header high-pressure side refrigerant flow paths 18a and 18b extending through the headers 4a and 4b in the vertical direction. Communicate with each. The high-temperature and high-pressure refrigerant that has flowed into the header high-pressure side refrigerant flow path 18a from the outside of the heat exchanger 1 flows into the high-pressure side refrigerant flow path 10a and passes through the high-pressure side refrigerant flow path 6 in the high-pressure side refrigerant flow path 10b. The refrigerant flows out of the heat exchanger 1 from the header high-pressure side refrigerant flow path 18b.
On the other hand, the low-pressure side refrigerant flow paths 12a and 12b communicate with the header low-pressure side refrigerant flow paths 20a and 20b extending through the headers 4a and 4b in the vertical direction. The low-temperature and low-pressure refrigerant that has flowed into the header low-pressure side refrigerant flow path 20a from the outside of the heat exchanger 1 flows into the low-pressure side refrigerant flow path 12a and passes through the low-pressure side flow path 8 and is refrigerant in the low-pressure side refrigerant flow path 12b. Flows out of the heat exchanger 1 from the header low-pressure side refrigerant flow path 20b.

Below, the effect | action (operation | movement) of the heat exchanger 1 of embodiment of this invention mentioned above is demonstrated.
In the process of assembling the heat exchanger 1 as a finished product, first, a plurality of round holes 6 and 8 are integrally formed by extruding or drawing a metal piece or clad material made of aluminum or the like. At this time, the round holes 6 (high-pressure side refrigerant flow path) and the round holes 8 (low-pressure side refrigerant flow path) are arranged in a staggered manner in the vertical direction, and the round hole 8 has a cross-sectional area of the round hole 6. More than the cross-sectional area, Preferably, it shape | molds so that ratio of the total cross-sectional area of the high-pressure side refrigerant flow path 6 and the total cross-sectional area of the low-pressure side refrigerant flow path 8 may be 1/3 or less.
Next, about this strip | belt-plate-shaped tube 2, the groove | channels 10a, 10b, 12a, and 12b are shape | molded by the milling etc. in the part adjacent to both end surfaces 2a and 2b. The strip-like tube 2 formed with the grooves 10a, 10b, 12a, 12b is inserted into the strip-like tube insertion grooves 14a, 14b of the headers 4a, 4b. At this time, the end faces 2a, 2b of the strip plate tube 2 are guided by strip plate tube guide grooves 16a, 16b provided in the depth surface inside the header 4a, 4b, and the depth surface inside the header 4a, 4b. Until it touches. Thereafter, the depth surfaces inside the headers 4a and 4b and the end surfaces 2a and 2b of the strip plate tube 2 are brazed, and the strip plate tube 2 and the headers 4a and 4b are assembled together.

As described above, according to the heat exchanger 1 according to the present embodiment, the high-pressure side refrigerant flow path 6 and the low-pressure side refrigerant flow path 8 of the strip plate tube 2 are integrally formed by extrusion or drawing. As a result, in the conventional heat exchanger, the two strip plate tubes on the high pressure side and the low pressure side are brazed, whereas in the present embodiment, the strip plate tube is used as one sheet and the number of parts is reduced. In addition, the number of brazing points can be reduced, and the functional reliability of the heat exchanger can be improved.
Further, according to the heat exchanger 1 according to the present embodiment, the high-pressure side refrigerant flow path 6 and the low-pressure side refrigerant flow path 8 of the strip plate tube 2 are arranged in a staggered manner in the vertical direction, so Can be reduced in thickness, and the overall weight can be reduced.
Furthermore, according to the heat exchanger 1 according to the present embodiment, when the strip plate tube 2 is inserted and attached to the back of the headers 4a and 4b, the grooves 10a, 10b, 12a provided in the strip plate tube 2 are attached. Since 12b forms the refrigerant | coolant flow path across thickness 13a, 13b, the strip plate-shaped tube 2 can play the role of the partition wall of a high voltage | pressure side and a low voltage | pressure side.
Moreover, according to the heat exchanger 1 by this embodiment, since the strip plate-shaped tube guide groove 16a, 16b is provided in the depth surface inside header 4a, 4b, the strip plate-shaped tube 2 is attached to header 4a, 4b. When attaching to the end, the end of the strip plate tube 2 is inserted along the guide grooves 16a and 16b, and the grooves 10a, 10b, 12a and 12b of the strip plate tube 2 are easily positioned inside the headers 4a and 4b. As a result, the assemblability can be improved. Moreover, the brazing property between the end surfaces 2a and 2b of the strip-like tube 2 and the depth surfaces inside the headers 4a and 4b can be improved.
Furthermore, according to the heat exchanger 1 according to the present embodiment, each of the low-pressure side cross-sectional areas is larger than each of the high-pressure side cross-sectional areas, and preferably the total cross-sectional area of the high-pressure side refrigerant flow path 6 and the low-pressure side Since the ratio of the total cross-sectional area of the side refrigerant flow path 8 is 1/3 or less, the flow velocity of the refrigerant flowing in the low pressure side refrigerant flow path 8 is reduced, and the pressure loss of the low temperature low pressure refrigerant is reduced. Can be reduced.

FIG. 4 shows a circuit diagram of a refrigeration cycle in a vapor compression supercritical refrigeration cycle apparatus according to an embodiment of the present invention.
Here, as the refrigerant used in the refrigeration cycle, for example, a refrigerant such as carbon dioxide having a critical point lower than the critical point of the alternative Freon R134a is used.
As shown in FIG. 4, a vapor compression supercritical refrigeration cycle apparatus 30 according to an embodiment of the present invention is a compressor 22 that compresses a refrigerant, a radiator 24, and the heat exchanger 1 of the above-described embodiment. And an internal heat exchanger 1. The refrigerant compressed in the compressor 22 is discharged to the radiator 24 and exchanged heat with the outside air, and then sent to the internal heat exchanger 1 provided downstream of the radiator 24. It has become.
The refrigerant sent to the internal heat exchanger 1 flows into the header high-pressure side refrigerant flow path 18a of the internal heat exchanger 1, and the high-pressure side refrigerant flow path 10a, the high-pressure side refrigerant flow path 6, and the high-pressure side refrigerant flow path 10b. The header high-pressure-side refrigerant flow path 18b is passed through in this order and is sent out from the internal heat exchanger 1.

Furthermore, the vapor compression supercritical refrigeration cycle apparatus 30 according to an embodiment of the present invention includes a high-pressure control valve 26, an evaporator 28, and a low-pressure receiver 29, and a high-temperature and high-pressure sent from the internal heat exchanger 1. The refrigerant is decompressed by the high-pressure control valve 26 and sent to the evaporator 28. The refrigerant sent out from the evaporator 28 is separated into a gas phase and a liquid phase by the low-pressure receiver 29, stored, and sent out from the low-pressure receiver 29.
The low-temperature and low-pressure refrigerant sent from the low-pressure receiver 29 flows into the header low-pressure side refrigerant flow path 20a of the internal heat exchanger 1, and the low-pressure side refrigerant flow path 12a, the low-pressure side refrigerant flow path 8, and the low-pressure side refrigerant flow path. 12b and the header low-pressure side refrigerant flow path 20b pass through in this order, are sent out from the internal heat exchanger 1, and are returned to the compressor 22.

By such a refrigeration cycle, the internal heat exchanger 1 passes through the high-pressure side refrigerant flow path of the internal heat exchanger 1 in the order of the flow path 18a, the flow path 10a, the flow path 6, the flow path 10b, and the flow path 18b. The high-temperature and high-pressure refrigerant and the low-temperature and low-pressure refrigerant passing through the low-pressure side refrigerant flow path of the internal heat exchanger 1 in the order of the flow path 20a, the flow path 12a, the flow path 8, the flow path 12b, and the flow path 20b By flowing in the opposite directions with respect to each other, heat exchange is performed between the two refrigerants.
Further, when the vapor compression supercritical refrigeration cycle apparatus 30 of the present embodiment is applied to a vehicle air conditioner, the internal heat exchanger 1 described above is used as an intercooler, and the evaporator 28 is used to cool the air in the vehicle interior. What is necessary is just to use the radiator 24 as a vehicle exterior heat exchanger.

  As described above, according to the vapor compression supercritical refrigeration cycle apparatus using the heat exchanger of the present invention and the vehicle air conditioner using the vapor compression supercritical refrigeration cycle apparatus, an intercooler is easily manufactured. Manufacturing cost can be reduced.

It is a whole exploded perspective view showing the heat exchanger by the embodiment of the present invention. It is AA sectional drawing of the heat exchanger by embodiment of this invention shown in FIG. It is BB sectional drawing in the strip plate-shaped tube part of the heat exchanger by embodiment of this invention shown in FIG. The example of the refrigerating cycle (supercritical refrigerating cycle) at the time of using the heat exchanger of this embodiment as an intercooler in the vehicle air conditioner using a vapor compression supercritical refrigerating cycle apparatus is shown. It is a disassembled perspective view of the conventional heat exchanger. It is CC sectional drawing in the conventional heat exchanger shown in FIG. It is DD sectional drawing in the strip plate-shaped tube part of the conventional heat exchanger shown in FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Heat exchanger 2 Band plate-like tube 4a, 4b Header 6 High pressure side refrigerant flow path 8 Low pressure side refrigerant flow path 10a, 10b High pressure side refrigerant flow path 12a, 12b Low pressure side refrigerant flow path 14a, 14b Band plate tube insertion groove 16a, 16b Strip plate-shaped tube guide grooves 18a, 18b Header high pressure side refrigerant flow path 20a, 20b Header low pressure side refrigerant flow path 22 Compressor 24 Radiator 26 High pressure control valve 28 Evaporator
29 Low pressure receiver 30 Vapor compression supercritical refrigeration cycle equipment

Claims (13)

A heat exchanger that performs heat exchange between a high-temperature and high-pressure refrigerant and a low-temperature and low-pressure refrigerant,
A strip-shaped tube member in which a high-pressure side refrigerant flow path through which a high-temperature and high-pressure refrigerant flows and a low-pressure side refrigerant flow path through which a low-temperature and low-pressure refrigerant flows are integrally formed;
A header member provided at both ends of the strip plate-shaped tube member, to which the strip plate-shaped tube member is inserted and fixed from the tube insertion groove;
The heat exchanger characterized by having.   2. The heat exchanger according to claim 1, wherein the strip-shaped tube member includes a plurality of high-pressure side refrigerant flow paths and a plurality of low-pressure side refrigerant flow paths.   The heat exchanger according to claim 1 or 2, wherein each of the high-pressure side refrigerant flow path and the low-pressure side refrigerant flow path of the strip-like tube member has a circular cross section.   The heat exchanger according to any one of claims 1 to 3, wherein a cross section of the low-pressure side refrigerant flow path of the strip-shaped tube member is formed larger than a cross section of the high-pressure side refrigerant flow path.   The heat exchanger according to any one of claims 2 to 4, wherein the high-pressure side refrigerant flow path and the low-pressure side refrigerant flow path of the strip plate-like tube member are alternately arranged in a staggered manner.   The strip plate-shaped tube member is inserted to the depth surface inside the header member, and the strip plate-shaped tube member is configured to partition the header member into a high-pressure side refrigerant channel and a low-pressure side refrigerant channel. The heat exchanger according to any one of claims 1 to 5.   The heat exchanger according to claim 6, wherein a tube guide groove is formed in a depth surface of the header member, and an end portion of the strip plate tube member is received by the tube guide groove.   The high-pressure side communication flow path that connects the high-pressure side refrigerant flow path of the band-shaped tube member and the high-pressure side refrigerant flow path of the header member to the side surface of the portion that is inserted into the header member of the band plate-shaped tube member, and the band shape 8. The heat exchanger according to claim 6, wherein a low-pressure side communication channel that connects the low-pressure side refrigerant channel of the tube member and the low-pressure side refrigerant channel of the header member is formed.   The heat exchanger according to any one of claims 6 to 8, wherein the tube insertion groove of the strip-shaped tube member is formed on the high-pressure side refrigerant flow path side with respect to the header central portion.   The heat exchanger according to any one of claims 1 to 9, wherein the strip-like tube member is formed by an extrusion process using an integral extruding material or formed by a drawing process using an integral drawing material.   The heat exchanger according to any one of claims 1 to 10, wherein the header member is formed by an extrusion process using an integral extrusion material, or formed by a drawing process using an integral drawing material. A vapor compression supercritical refrigeration cycle apparatus that forms a refrigeration cycle by using a supercritical fluid as a refrigerant, a compressor that compresses the refrigerant, a radiator, an evaporator, and a decompression unit,
An internal heat exchanger that exchanges heat between the high-pressure side refrigerant between the radiator and the decompression means and the low-pressure side refrigerant sucked into the compressor is provided as the internal heat exchanger. A vapor compression supercritical refrigeration cycle apparatus using the heat exchanger according to any one of items 1 to 11.   A vehicle air conditioner using the vapor compression supercritical refrigeration cycle apparatus according to claim 12.

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