JP2005030741A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger that can reduce flow resistance and prevent a longitudinal drift of fluid by arranging a flow dividing plate of simple shape in a header tank. <P>SOLUTION: A longitudinal end of the header tank 140a at one end has an inlet 190a for leading in a refrigerant. A flow part 151 is divided into inlet passages 151a and other passages 151 and 151b, and in one inlet passage 151a, the flow dividing plate 170a is arranged to divide the refrigerant flowing into the inlet 190a at least into two toward a plurality of stacked tubes 110. Flow resistance can be reduced and a longitudinal fluid drift can be prevented. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a heat exchanger, and is suitable for application to, for example, a gas cooler or an evaporator used in a supercritical refrigeration cycle apparatus.

  Conventionally, what is shown by patent document 1 is known as this kind of heat exchanger, for example. This is a heat exchanger in which a plurality of tubes are stacked and header tanks are provided at both ends of the tubes. The header tank on one end side is provided with an inlet side passage and an outlet side passage. The distribution plate is arranged along the longitudinal direction, and the inlet side passage is divided into two, and divided into an inlet pipe connection passage to which the inlet pipe is connected and a tube connection passage connected to the tube connected thereto, A plurality of openings having different flow resistances are formed in the distribution plate.

As a result, the inflow amount of the refrigerant that is the fluid into the tube is made uniform regardless of the connection position of the inlet pipe or the outlet pipe and the header tank. The refrigerant enters the inlet pipe connection passage to which the inlet pipe of the header tank is connected, and then passes through all openings in the tube connection passage connected to the tube through openings having different flow resistances formed in the distribution plate. The refrigerant is made to flow evenly, and the refrigerant is made to evenly flow into each tube (see, for example, Patent Document 1).
JP 2001-255095 A

However, in the heat exchanger in the supercritical refrigeration cycle apparatus using a refrigerant such as CO ₂ as the refrigerant, according to the configuration as described in Patent Document 1, for example, the refrigerant at the connection position between the inlet pipe and the header tank In the case where the inlet is located at a position below the lower end of the tube and provided at one end in the longitudinal direction of the header tank, the refrigerant flowing from the inlet, particularly at a low flow rate, is due to the specific gravity of the refrigerant. In the vicinity of the inflow port, the refrigerant flows to the lower side of the inlet pipe connection passage so as to be farther from the lower end of the tube, and is circulated so that the amount of refrigerant increases in the longitudinal direction rear side of the header tank. As a result, there is a problem that the refrigerant is not evenly distributed to the tubes even if the distribution plate is provided with openings having different flow resistances.

  On the other hand, when the inlet is provided at a position above the upper end of the tube, the refrigerant flowing in from the inlet flows into the vicinity of the inlet, that is, on the front side in the longitudinal direction of the header tank due to the specific gravity of the refrigerant. It is distributed to increase the amount. As a result, the refrigerant is not evenly distributed to the tubes as described above.

  Also, in order to make the flow resistance of the fluid flow path from the inlet pipe through the tube to the outlet pipe uniform, in addition to the opening with different flow resistance, the other end side header tank (U-turn side) Since the rectifying plate having the communication portion is provided and the inlet side passage and the outlet side passage are configured to be partitioned, by having flow resistance in these openings and the communication portion, the heat exchanger as a whole There is a problem that distribution resistance increases.

  Accordingly, an object of the present invention is to take the above-mentioned points into consideration, and by disposing a simple-shaped flow dividing plate in the header tank, the flow resistance is small and fluid drift in the longitudinal direction is prevented. An object of the present invention is to provide a heat exchanger that makes it possible.

In order to achieve the above object, the technical means described in claims 1 to 8 are employed. That is, in the invention according to claim 1, a plurality of stacked tubes (110) and a pair of header tanks extending in the stacking direction of the tubes (110) by forming a flow portion (151) through which a fluid flows are formed. 140a, 140b)
In the heat exchanger in which both ends of the tube (110) in the longitudinal direction are joined to the pair of header tanks (140a, 140b), and the flow part (151) and the inside of the tube (110) communicate with each other.
One end of the header tank (140a) on one end side in the longitudinal direction is provided with an inflow port (190a) through which a fluid flows, and the flow portion (151) includes an inlet-side passage (151a) and other passages (151, 151b). And a flow dividing plate that is divided into at least one half of the fluid flowing in from the inflow port (190a) toward the plurality of tubes (110) stacked in the one inlet side passage (151a). (170a, 170b, 170c) is provided.

According to the first aspect of the present invention, the flow dividing plates (170a, 170b, 170c) are divided at least in half toward the plurality of tubes (110) in which the fluid flowing in from the inflow port (190a) is stacked. For example, in a heat exchanger configured in a supercritical refrigeration cycle apparatus that uses a refrigerant such as CO ₂ as a fluid, the header tanks (140a and 140b) are arranged in the inlet-side passage (151a) due to the specific gravity of the refrigerant. In the longitudinal direction, there is a drift in the vicinity of the inflow port (190a) and the back side in the longitudinal direction, but it is possible to prevent the drift by the diversion plates (170a, 170b, 170c) that are divided in two. The refrigerant can be evenly distributed to each tube (110).

  In the invention according to claim 2, when the inflow port (190a) is disposed above the upper end of the tube (110), the fluid flowing in from the inflow port (190a) has a header tank (140a) on one end side. The flow-dividing plates (170a, 170b, 170c) are arranged in the inlet-side passage (151a) so as to flow in a large amount toward the back in the longitudinal direction.

  Specifically, when the fluid flowing from the header tank (140a) to the tube (110) circulates in the direction of gravity, the fluid is directed to the header tank (140a on one end side). ) Is arranged in the inlet side passageway (151a) so as to flow in a large amount toward the back in the longitudinal direction of the longitudinal direction, so that uneven flow can be prevented and each tube (110). The refrigerant can be evenly divided.

  In the invention according to claim 3, when the inlet (190a) is disposed below the lower end of the tube (110), a large amount of fluid flowing in from the inlet (190a) is directed toward the front in the longitudinal direction. The flow dividing plates (170a, 170b, 170c) are arranged in the inlet side passageway (151a) so as to flow.

  According to the third aspect of the invention, conversely, when the fluid flowing from the header tank (140a) to the tube (110) flows in the antigravity direction, the fluid is at one end of the header tank (140a). Since the flow dividing plates (170a, 170b, 170c) are arranged in the inlet side passageway (151a) so as to flow in a large amount toward the front side in the longitudinal direction of the tube, uneven flow can be prevented and each tube (110). The refrigerant can be evenly divided.

  In the invention according to claim 4, the flow dividing plates (170 a, 170 b, 170 c) are formed of a plate-like plate material extending in the longitudinal direction, and one or a plurality of flow dividing plates are arranged in the inlet side passage (150 a). It is characterized by. According to the invention described in claim 4, by forming the flat plate material extending in the longitudinal direction so as to be divided into at least two parts, openings having different flow resistances are formed as in Patent Document 1. The flow resistance does not increase by diverting without being performed. In addition, the flow dividing plates (170a, 170b, 170c) can be formed with a simple shape.

  In the invention according to claim 5, the flow dividing plates (170 a, 170 b, 170 c) form a concave concave surface portion (170 d) on a flat plate material, and one or a plurality of flow dividing plates (170 a) are arranged in the inlet side passage (151 a). It is characterized by that. According to the third aspect of the present invention, even if the concave concave surface portion (170d) is formed, the flow resistance does not increase as in the fourth aspect. In addition, the flow dividing plates (170a, 170b, 170c) can be formed with a simple shape.

  The invention according to claim 6 is characterized in that the flow dividing plates (170a, 170b, 170c) are disposed in the inlet-side passage (151a) so as to be inclined in the longitudinal direction of the header tank (140a) on one end side. Yes. According to the invention described in claim 6, for example, by inclining the flow dividing plates (170a, 170b, 170c) so that the inlet-side passage (151a) expands toward the other end in the longitudinal direction, Many fluids can flow to the side. Conversely, by inclining the flow-dividing plates (170a, 170b, 170c) so that the inlet-side passage (151a) shrinks toward the other end in the longitudinal direction, a large amount of fluid is placed near the inlet (190a). Can flow. Accordingly, the flow dividing plates (170a, 170b, 170c) can be formed with a simpler shape.

  In the invention according to claim 7, a plurality of tubes (110) stacked in the longitudinal direction of the header tanks (140a, 140b) are arranged in the air flow direction so that a plurality of the outgoing tube groups and the outgoing tube groups are provided. And a plurality of return tube groups through which fluid flows in the opposite direction, the inside of the outgoing tube group and the return tube group and the flow part (151) of the pair of header tanks (140a, 140b) communicate with each other The heat exchanger is a U-turn type.

  Specifically, according to the seventh aspect of the present invention, a plurality of tubes (110) stacked in the longitudinal direction of the header tank (140a, 140b) are passed, and a tube group and a return tube group are formed. In the heat exchanger heat exchanger in which the flow of fluid is a front-rear U-turn system, the flow is prevented by arranging the flow dividing plates (170a, 170b, 170c) that are divided into at least two parts in the inlet side passage (151a). In addition to being able to prevent, the refrigerant can be evenly distributed to each tube (110).

The invention according to claim 8 is characterized in that the fluid is CO ₂ . According to invention of Claim 8, it is because the heat exchanger of this invention is suitable for using for the system used as high pressure conditions, such as a supercritical refrigeration cycle apparatus.

  In addition, the code | symbol in the bracket | parenthesis of each said means shows the correspondence with the specific means of embodiment mentioned later.

(First embodiment)
Hereinafter, the heat exchanger in 1st Embodiment of this invention is demonstrated based on FIG. 1 thru | or FIG. FIG. 1 is a perspective view showing an overall configuration of a gas cooler 100 which is a heat exchanger in which the present invention is applied to a supercritical refrigeration cycle apparatus, and FIG. 2 is a cross-sectional view showing a cross section taken along line AA shown in FIG. FIG. 3 is a longitudinal sectional view showing a configuration in the header tank 140a, and FIG. 4 is a schematic perspective view showing a refrigerant flow path configuration of the gas cooler 100.

First, the supercritical refrigeration cycle apparatus is a refrigeration cycle using CO _2, ethylene, ethane, nitric oxide or the like as a refrigerant that is a fluid, and the high pressure side pressure becomes the critical pressure of the refrigerant. In the present embodiment, the present invention relates to a gas cooler 100 applied to a supercritical refrigeration cycle using CO ₂ as a refrigerant, and heat exchange is performed between a high-pressure refrigerant compressed by a compressor and a critical pressure or higher and air. It is a heat exchanger for cooling.

  As shown in FIG. 1, the gas cooler 100 is composed of a core portion 101 and upper and lower header tanks 140a and 140b, and each member constituting these is made of aluminum or an aluminum alloy, and is fitted, caulked, fixed to a jig, etc. Each member is joined to the brazing material previously assembled on the surface of each member by integral brazing.

  The core portion 101 has a plurality of tubes 110 through which a refrigerant flows and a plurality of fins 120 formed in a corrugated shape alternately stacked, and the outermost fins 120 on the left and right sides are further U-shaped in cross section. A side plate 130 is disposed as a strength member that opens to the front. The tubes 110 and the fins 120 are provided in a plurality of rows in the width direction W of the gas cooler 100 (for example, two rows on the upstream side and the downstream side of the air flow). Here, the plurality of tubes 110 arranged on the upstream side of the air flow is a return tube group, and the plurality of tubes 110 arranged on the downstream side thereof is a tube group, and the return tube group goes to the tube group. In the tube group, the flow direction of the refrigerant circulating inside flows in the opposite direction.

  A pair of header tanks 140a and 140b extending in the tube stacking direction L (also referred to as the longitudinal direction) are provided at the ends of the tubes 110 in the longitudinal direction. As shown in FIG. 2, the header tanks 140 a and 140 b include a tank plate 150, a caulking plate 160, and an end plate 180.

  The tank plate 150 is formed by pressing a plate-like member to form a plurality of cross-sectional shapes of the flow part 151 in a substantially U shape. The caulking plate 160 is formed by pressing a plate-like member into a substantially U-shape having claw portions 160a at both ends in the short side direction, and a tube insertion hole at a position corresponding to the end portion of the tube 110. A plurality of 160a are provided. Note that the end of the tube 110 is joined to the tube insertion hole 160a so that the flow portion 151 and the inside of the tube 110 communicate with each other.

  The end plate 180 is a member for closing both ends of the flow portion 151 formed by the tank plate 150 and the caulking plate 160. An inlet 190a through which the refrigerant flows into the header tank 140a and an outlet 190b through which the heat-exchanged refrigerant flows out of the header tank 140a are formed at one end of the upper header tank 140a. Although not shown, an inlet pipe and an outlet pipe are joined to the inlet 190a and the outlet 190b, respectively.

  A partition member 200 for partitioning the circulation portion 151 into an inlet-side passage 151a and an outlet-side passage 151b is provided inside the upper header tank 140a. The partition member 200 is formed so that its cross section is substantially convex and is sandwiched between the tank plate 150 and the caulking plate 160.

  Further, a flow dividing plate 170a is provided in the inlet side passage 151a. The flow dividing plate 170a is a member for dividing the refrigerant flowing in from the inlet 190a into two parts, and is formed of a flat plate material extending in the stacking direction of the tubes 110 as shown in FIGS. is doing. In addition, the length of the longitudinal direction of the flow dividing plate 170a is formed so that it may extend from the vicinity of the inflow port 190a to the substantially middle part with respect to the lamination direction of the tube 110, as shown in FIG.

  That is, the flow dividing plate 170a is arranged so that a large amount of the refrigerant flowing in from the inlet 190a flows in the inlet side passage 151a toward the back in the longitudinal direction, and the refrigerant flows from the vicinity of the inlet 190a to the back in the longitudinal direction. Is divided into two minutes. As a result, when there is no flow dividing plate 170a, due to the specific gravity of the refrigerant, there is generally a drift of the refrigerant between the rear side in the longitudinal direction and the vicinity of the inlet 190a. However, by providing the flow dividing plate 170a having a simple shape, Can be prevented.

  On the other hand, a flow passage 151 is formed in the lower header tank 140b for allowing the refrigerant flowing from the inlet side passage 151a to the inside of the tube 110 to make a U-turn toward the outlet side passage 151b. Next, a method for assembling the header tanks 140a and 140b having the above configuration will be described.

  First, in the upper header tank 140a, the flow dividing plate 170a, the partition member 200, and the end plate 180 are set in predetermined positions in the caulking plate 160, and after the tank plate 150 is stacked, the claw portion 160a of the caulking plate 160 is The header tank 140a is formed by pressing down the upper surface of the tank plate 150.

  In the lower header tank 140b, the end plate 180 is set in a predetermined position in the caulking plate 160, and after the tank plate 150 is stacked, the claw portion 160a of the caulking plate 160 is caulked to press down the upper surface of the tank plate 150. A tank 140b is formed. Then, the end portions of the tubes 110 and the end portions of the side plates 120 are inserted into the tube insertion holes 160b of the header tanks 140a and 140b, and these members are joined by integral brazing.

  Next, the operation of the gas cooler 100 having the above configuration will be described. By the way, the gas cooler 100 of this embodiment has an inflow port 190a connected to a discharge side of a compressor (not shown) and an outflow port 190b connected to an expansion valve (not shown). Therefore, description will be made based on the flow path configuration of the gas cooler 100 shown in FIG. As shown in FIG. 4, the high-temperature and high-pressure refrigerant discharged from the compressor flows into the inlet-side passage 151a from the inlet 190a, and flows into the stacked tubes 110 by the flow dividing plates 170a in the inlet-side passage 151a. The flow is divided into two parts, distributed to the tubes 110 on the downstream side of the air flow, flows downward, flows into the flow passage 151 in the lower header tank 140b, and flows into the flow passage 151. It makes a U-turn, flows into each tube 110 on the upstream side of the air flow, flows upward, flows into the upper outlet side passage 151b, and flows out from the outlet 190b. During this time, the refrigerant is cooled by exchanging heat with external air in the core portion 101.

According to the gas cooler 100 of the first embodiment described above, the flow dividing plate 170a that is divided into at least two parts toward the plurality of tubes 110 in which the high-temperature and high-pressure refrigerant that has flowed in from the inlet 190a is stacked is disposed in the inlet-side passage 151a. For example, in a heat exchanger configured in a supercritical refrigeration cycle apparatus that uses a refrigerant such as CO ₂ as a fluid, an inlet 190a is formed with respect to the longitudinal direction of the header tank 140a due to the specific gravity of the refrigerant. Although drift occurs between the vicinity and the back side in the longitudinal direction, drift can be prevented by the flow dividing plate 170a that is divided into two, and the refrigerant can be evenly divided into the tubes 110.

  Further, when the fluid flowing from the upper header tank 140a to the tube 110 flows in the direction of gravity as in the present embodiment, a large amount of fluid flows toward the far side in the longitudinal direction of the one end side header tank 140a. Further, by arranging the flow dividing plate 170a in the inlet side passage 151a, it is possible to prevent the drift and to distribute the refrigerant equally to each tube 110.

  In addition, since the flow dividing plate 170a is formed of a flat plate material extending in the longitudinal direction, the flow resistance is increased by dividing the flow without forming openings having different flow resistances as in the conventional Patent Document 1. There is nothing. Moreover, the flow dividing plate 170a can be formed with a simple shape.

The fluid uses CO ₂ refrigerant. This is because the heat exchanger of the present invention is suitable for use in a system having high pressure conditions such as a supercritical refrigeration cycle apparatus.

(Second Embodiment)
In the first embodiment described above, the length in the longitudinal direction of the flow dividing plate 170a is formed so as to extend from the vicinity of the inflow port 190a to substantially the middle with respect to the stacking direction of the tubes 110, and is disposed in the inlet side passage 151a. However, the present invention is not limited to this, and as shown in FIG. 5, the length of the flow dividing plate 170a in the longitudinal direction may be formed so that a gap is formed at both ends in the inlet side passage 151a.

  According to this, the refrigerant flowing in from the inflow port 190a can be divided into two by the flow dividing plate 170a in the vicinity of the inflow port 190a and the back side in the longitudinal direction of the inlet side passage 151a. Accordingly, the same effects as those of the first embodiment are obtained.

(Third embodiment)
In the above embodiment, the flat plate-like flow dividing plate 170a is disposed in the inlet side passage 151a in the substantially horizontal direction. However, the present invention is not limited to this, and the flow dividing plate 170a is inclined in the longitudinal direction to enter the inlet side passage 151a. It may be arranged. According to this, for example, as shown in FIG. 6, a large amount of fluid flows in the longitudinal direction rear side by inclining the flow dividing plate 170 a so that the inlet-side passage 151 a expands toward the other end in the longitudinal direction. be able to. Conversely, by inclining the flow dividing plate 170a so that the inlet-side passage 151a contracts toward the other end in the longitudinal direction, a large amount of fluid can flow near the inlet 190a. Thereby, the flow dividing plate 170a can be formed with a simpler shape.

(Fourth embodiment)
In the above embodiment, one flow dividing plate 170a is disposed in the inlet side passage 151a. However, the present invention is not limited to this, and a plurality of flow dividing plates 170a may be provided. In this embodiment, as shown in FIGS. 7 and 8, two flow dividing plates 170b and 170c are disposed. Specifically, as shown in FIG. 7, a first diverting plate 170b and a second diverting plate 170c are stacked on the lower end of the header tank 150, and a concave concave surface portion 170d is formed at a position corresponding to the outlet 190a. So that each flow path is formed.

  Then, as shown in FIG. 8, the first flow dividing plate 170b is formed to have such a length as to flow toward the back side in the longitudinal direction, and the second flow dividing plate 170c is flowed to the substantially intermediate side in the longitudinal direction. Is formed. That is, in this embodiment, it forms so that it may be divided into about 3 minutes toward the lamination direction of the tube 110. FIG.

  According to this, drift can be prevented more than in the above embodiment, and even if the concave concave surface portion 170d is formed, the flow resistance does not increase. Moreover, the flow dividing plates 170b and 170c can be formed with a simple shape.

(Fifth embodiment)
In the above embodiment, the inflow port 190a and the outflow port 190b are formed in the upper header tank 140a, and the refrigerant flowing in from the inflow port 190a is divided into the tube 110 in the gravity direction from the inlet side passage 151a. In addition, when the inlet 190a and the outlet 190b are formed on the lower side and are divided into the tube 110 in the antigravity direction from the inlet side passage 151a, as shown in FIG. 9, the flow is divided into the lower header tank 140a. A plate 170a may be provided.

  According to this, the flow dividing plate 170a is arranged in the inlet-side passage (151a) so that a large amount of the refrigerant flowing in from the inlet 190a flows toward the front side in the longitudinal direction of the one-end header tank 140a. In addition to being able to prevent, the refrigerant can be evenly distributed to each tube 110.

(Other embodiments)
In the above embodiment, in the other end side header tank 140b, only the refrigerant that has flowed into the circulation portion 151 from the tube 110 on the downstream side of the air flow is U-turned, but this portion also has one end having the flow dividing plate 170a. A side header tank 140a may be provided and diverted.

  However, at this time, as shown in FIG. 10, the header tank 140a having the flow dividing plate 170a is disposed at both ends of the tube 110 so that the lower outlet 190b and the inlet 190a communicate with each other. Thereby, also in the tube 110 on the upstream side of the air flow, drift can be prevented and the refrigerant can be evenly distributed to each tube 110.

Moreover, in the above embodiment, although this invention was applied to the gas cooler 100 in a supercritical refrigeration cycle apparatus as a heat exchanger, you may apply to the evaporator which evaporates a refrigerant | coolant. Furthermore, the present invention is not limited to the supercritical refrigeration cycle apparatus using CO ₂ refrigerant, but can be widely applied to a normal refrigeration cycle and other heat exchangers used for vehicle engines.

It is a perspective view showing the whole gas cooler 100 composition in a 1st embodiment of the present invention. It is AA sectional drawing shown in FIG. It is a longitudinal cross-sectional view which shows the structure in the header tank 140a in 1st Embodiment of this invention. It is a schematic perspective view which shows the flow-path form of the gas cooler 100 in 1st Embodiment of this invention. It is a longitudinal cross-sectional view which shows the structure in the header tank 140a in 2nd Embodiment of this invention. It is a longitudinal cross-sectional view which shows the structure in the header tank 140a in 3rd Embodiment of this invention. It is a longitudinal cross-sectional view which shows the structure of the header tank 140a in 4th Embodiment of this invention. It is a longitudinal cross-sectional view which shows the structure of the header tank 140a in 4th Embodiment of this invention. It is a longitudinal cross-sectional view which shows the structure of the header tank 140a in 5th Embodiment of this invention. It is a schematic perspective view which shows the structure of the gas cooler 100 in other embodiment.

Explanation of symbols

110 ... Tubes 140a, 140b ... Header tank 151 ... Distribution part (other passages)
151a ... Inlet side passage 151b ... Outlet side passage (other passages)
170a ... Diversion plate 170b ... First diversion plate (diversion plate)
170c ... 2nd diversion plate (diversion plate)
170d ... concave part 190a ... inlet

Claims (8)

A plurality of stacked tubes (110);
A pair of header tanks (140a, 140b) extending in the stacking direction of the tubes (110) by forming a flow part (151) through which fluid flows inside;
In the heat exchanger in which both ends in the longitudinal direction of the tube (110) are joined to the pair of header tanks (140a, 140b), and the flow part (151) and the inside of the tube (110) communicate with each other.
One end of the header tank (140a) on the one end side in the longitudinal direction is provided with an inlet (190a) through which a fluid flows, and the circulation section (151) includes an inlet-side passage (151a) and other passages (151). 151b), and at least one of the inlet-side passages (151a) is divided into a plurality of tubes (110) stacked with the fluid flowing in from the inlet (190a). A heat exchanger characterized in that a flow dividing plate (170a, 170b, 170c) to be divided is disposed.   When the inflow port (190a) is disposed above the upper end of the tube (110), the fluid flowing in from the inflow port (190a) is deep in the longitudinal direction of the header tank (140a) on the one end side. The heat exchanger according to claim 1, wherein the flow dividing plates (170a, 170b, 170c) are arranged in the inlet side passage (151a) so as to flow in a large amount toward the front.   When the inlet (190a) is disposed below the lower end of the tube (110), the flow dividing plate is arranged so that a large amount of fluid flowing in from the inlet (190a) flows toward the front in the longitudinal direction. The heat exchanger according to claim 1, wherein (170a, 170b, 170c) is disposed in the inlet-side passage (151a).   The said flow dividing plate (170a, 170b, 170c) is formed with the flat plate-shaped board | plate material extended in the longitudinal direction, and 1 sheet or multiple sheets were arrange | positioned by the said entrance side channel | path (151a). Or the heat exchanger of Claim 3.   The flow dividing plates (170a, 170b, 170c) are characterized in that a flat concave plate portion (170d) is formed on a flat plate material, and one or a plurality of flow dividing plates (170a) are arranged in the inlet-side passage (151a). The heat exchanger according to claim 2 or claim 3.   The flow dividing plates (170a, 170b, 170c) are disposed in the inlet-side passage (151a) so as to be inclined in the longitudinal direction of the header tank (140a) on the one end side. Item 6. The heat exchanger according to any one of Items 5.   The plurality of tubes (110) stacked in the longitudinal direction of the header tanks (140a, 140b) flow back and forth in the air flow direction and flow in the opposite direction to the plurality of going tube groups and the going tube group. A plurality of return tube groups are formed, and the inside of the going tube group and the return tube group and the flow part (151) of the pair of header tanks (140a, 140b) are communicated with each other to form a front-rear U-turn system. The heat exchanger according to claim 1, wherein the heat exchanger is a heat exchanger. The fluid heat exchanger according to any one of claims 1 to 7, characterized in that a CO _2.

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