JP2006329511A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To further improve heat exchanging performance in a heat exchanger with a plurality of cores disposed in an external fluid flow direction so that an internal fluid and an external fluid form counterflow. <P>SOLUTION: A radiator 20 comprises a communicating passage 25A allowing the inside of a second head tank 242 on the terminal side of a first core 21 downstream of cooling air to communicate with the inside of a third head tank 233 on the starting edge side of a second core 22 upstream of the cooling air. A refrigerant flow direction in the first core 21 is made the same as a refrigerant flow direction in the second core 22. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a heat exchanger in which an internal fluid changes sensible heat by heat exchange with an external fluid.

  As a prior art, there is a heat exchanger disclosed in Patent Document 1 below. This heat exchanger is a radiator (gas cooler) that circulates a refrigerant pressurized to a critical pressure or more inside and radiates heat to air flowing outside to cool the refrigerant.

  Since the refrigerant pressurized above the critical pressure does not condense even when cooled, the refrigerant changes sensible heat by heat exchange, and the temperature change inside the heat exchanger is large.

  Therefore, in the above-described heat exchanger according to the prior art, the inside of the header tank connected to the plurality of laminated porous flat tubes is divided, and the first half composed of the downstream half of the external air flow of the tube stack (a plurality of tube rows). The flow direction of the refrigerant is reversed between the core part (first heat exchange part) and the second core part (second heat exchange part) composed of the outer air flow upstream half.

  And after cooling the high temperature refrigerant | coolant which flows into the 1st core part and flows in the same direction (what is called all passes) with the external air which passed the 2nd core part, a refrigerant | coolant is made U-turn to the external air flow upstream. When the second core part flows in the same direction (all paths in the direction opposite to the first core part), heat exchange is performed with the external air passing through the second core part.

That is, by making a U-turn so that the refrigerant is opposed to the external air flow, a temperature difference between the refrigerant and the external air is formed in both core portions, thereby ensuring good heat exchange efficiency.
Japanese Patent Laid-Open No. 10-288476

  However, in the above-described conventional heat exchanger, the external air that has passed near the refrigerant flow start end portion of the second core portion passes near the refrigerant flow end portion of the first core portion. Since the temperature difference between the refrigerant in the vicinity of the end portion of the first core portion and the refrigerant in the vicinity of the start end portion of the second core portion is small, the temperature difference between the refrigerant and the external air is relatively close in the vicinity of the end portion of the first core portion. Get smaller.

  Therefore, although the refrigerant is U-turned so as to be opposed to the external air flow, there is a problem that it is difficult to ensure good heat exchange efficiency in the vicinity of the terminal portion of the first core portion.

  Further, in the header tank connected to the start end side of the first core part and the end side of the second tank, the cooled refrigerant after the heat exchange is reheated by the high-temperature refrigerant before the heat exchange, thereby reducing the heat exchange performance. There is also the problem of doing.

  This invention is made | formed in view of the said point, and it aims at providing the heat exchanger which can further improve heat exchange performance.

In order to achieve the above object, in the invention described in claim 1,
A plurality of tubes (211) are laminated, and the internal fluid flowing in the same direction through the plurality of tubes (211) and the external fluid flowing outside the plurality of tubes (211) are subjected to heat exchange, and the internal fluid A first core (21) that changes the sensible heat of
A first header tank (231) connected to a plurality of tubes (211) of the first core (21) on the start end side of the first core (21);
A second header tank (242) connected to a plurality of tubes (211) of the first core (21) on the terminal side of the first core (21);
A plurality of tubes (221) are stacked, arranged in parallel upstream of the first core (21) in the direction of external fluid flow, and the first core (21) that circulates in the plurality of tubes (221) in the same direction. A second core (22) that changes the sensible heat of the internal fluid by exchanging heat between the internal fluid after passing through the external fluid flowing outside the plurality of tubes (221),
A third header tank (233) connected to the plurality of tubes (221) of the second core (22) on the start end side of the second core (22);
A fourth header tank (244) connected to the plurality of tubes (221) of the second core (22) on the terminal side of the second core (22);
A communication path (25A) communicating the second header tank (242) and the third header tank (233);
The flow direction of the internal fluid in the first core (21) and the flow direction of the internal fluid in the second core (22) are substantially the same.

  According to this, the internal fluid which circulated through the plurality of tubes (211) of the first core (21) is guided to the second core (22) via the communication path (25A), and the second core (22) It flows through the plurality of tubes (221) in a direction substantially the same as the flow direction in the first core (21).

  That is, in the flow direction of the external fluid, the first core (21) and the second core (22) are arranged in parallel with each other on the internal flow start side and on the internal flow end side.

  Therefore, it is easy to form a temperature difference between the internal fluids of the portions where the first core (21) and the second core (22) are arranged side by side in the entire area of both cores (21, 22). Thus, the first and second cores (21, 22) are arranged so that the internal fluid is opposed to the external fluid, and the temperature of the internal fluid and the external fluid is increased over the entire area of both cores (21, 22). A relatively large difference can be ensured and the heat exchange efficiency can be improved.

  Further, the first header tank (231) on the start end side of the first core (21) and the fourth header tank (244) on the end side of the second core (22) can be separated from each other. Therefore, it is possible to prevent a decrease in heat exchange performance due to heat transfer between the header tanks (231, 244).

  In this way, heat exchange performance can be further improved in the heat exchanger in which the internal fluid changes in sensible heat by heat exchange with the external fluid.

  In the second aspect of the present invention, the communication path (25A) is disposed entirely between the formation surface of the first core (21) and the formation surface of the second core (22). It is a feature.

  According to this, even if the communication path (25A) communicating between the second header tank (242) and the third header tank (233) is provided, the size of the heat exchanger is increased in the flow direction of the external fluid. Can be suppressed.

  Further, as in the invention described in claim 3, the communication passage (25A) is easily formed in the piping member (25) connected to the second header tank (242) and the third header tank (233). Can do.

  In the invention according to claim 4, the piping member (25) is characterized in that heat exchange fins (251) are formed on the outer periphery.

  According to this, heat exchange between the internal fluid flowing through the communication passage (25A) in the piping member (25) and the external fluid can be promoted. Therefore, the heat exchange performance can be further improved.

  In the invention according to claim 5, the reinforcing member (213) that reinforces at least one of the first core (21) and the second core (22) is provided, and the communication path (25 B) includes the reinforcing member ( 213).

  According to this, the member which forms a communicating path (25B) can be used as the reinforcing member (213) of a core (21, 22). Therefore, an increase in the size of the heat exchanger can be suppressed by providing the communication path (25B).

  Further, the invention according to claim 6 is characterized in that the communication path (25A) is formed in a straight line.

  According to this, the pressure loss of the internal fluid flowing from the second header tank (242) to the third header tank (233) can be reduced.

  Further, in the invention according to claim 7, the external fluid is air, and the external fluid is heated in the first core (21) and the second core (22) by heat exchange with the internal fluid, and is then indoors. It is characterized by being blown out.

  According to this, the room can be heated by the external fluid blown into the room.

  Then, as in the invention described in claim 8, out of the external fluid passing through the first core (21), the external fluid passing near the first header tank (231) is blown out to the lower side in the room, and the second By blowing the external fluid passing near the header tank (242) to the upper side of the room, it is possible to easily form a head-and-foot heat type temperature distribution in which the lower side has a higher blowing temperature than the upper side.

In the invention according to claim 9,
The second core (22) is disposed downstream of the other heat exchanger (90) in the flow direction of the external fluid, and a part of the second core (22) is connected to the other heat exchanger (90) in the flow direction of the external fluid. It is arranged side by side,
A portion of the second core (22) near the third header tank (233) is arranged side by side so as to overlap with the other heat exchanger (90).

  According to this, the external fluid heat-exchanged by the other heat exchanger (90) passes through the start end side part (part close to the third header tank (233)) of the second core (22), and the second The external fluid that has not been heat-exchanged by the other heat exchanger (90) passes through the end side portion of the core (22) (part close to the fourth header tank (244)).

  Accordingly, even when other heat exchangers (90) are arranged in parallel on the upstream side of the external fluid, a relatively large temperature difference between the internal fluid and the external fluid is ensured across the two cores (21, 22). Easy to do.

  The invention according to claim 10 is characterized in that the internal fluid is a fluid pressurized to a critical pressure or higher.

  An internal fluid pressurized to a critical pressure or higher, that is, an internal fluid in a supercritical state, does not change its latent heat even if it exchanges heat with an external fluid, and changes its sensible heat. Therefore, it is extremely effective to apply the present invention to a heat exchanger in which the internal fluid has a critical pressure or higher.

  In addition, the code | symbol in the parenthesis attached | subjected to each said means is an example which shows a corresponding relationship with the specific means as described in embodiment mentioned later.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(First embodiment)
FIG. 1 is a perspective view showing a schematic configuration of a radiator 20 that is a heat exchanger in the first embodiment to which the present invention is applied, and FIG. 2 explains the flow directions of the internal fluid and the external fluid of the radiator 20. FIG. 3 is a top view for explaining the flow direction of the internal fluid and the external fluid of the radiator 20.

FIG. 4 is a schematic diagram showing a schematic configuration of a supercritical refrigeration cycle 1 using carbon dioxide (CO ₂ ) as a refrigerant and provided with a radiator 20 to which the present invention is applied.

  In FIG. 2, in order to facilitate understanding of the flow direction of the internal fluid, the components of the radiator 20 are partially separated from FIGS. 1 and 3.

  In FIG. 4, 10 is a compressor that compresses the refrigerant, and 20 is a radiator (gas cooler) that cools the refrigerant compressed by the compressor 10. 30 is a pressure control valve (pressure reducing valve) that depressurizes the refrigerant flowing out of the radiator 20 and controls the refrigerant pressure on the high pressure side. The refrigerant pressure on the high pressure side refers to the refrigerant pressure before being depressurized by the pressure control valve 30 extending from the discharge side of the compressor 10 to the refrigerant inlet side of the pressure control valve 30.

  Reference numeral 40 denotes an evaporator that evaporates (liquid phase) refrigerant depressurized by the pressure control valve 30. Reference numeral 50 denotes a gas that is separated from the refrigerant flowing out of the evaporator 40 into a gas phase refrigerant and a liquid phase refrigerant. It is an accumulator (gas-liquid separation means) that causes the refrigerant to flow out to the suction side of the compressor 10 and stores excess refrigerant in the supercritical refrigeration cycle 1.

  Reference numeral 60 denotes an internal heat exchanger that exchanges heat between the low-pressure side refrigerant flowing out of the accumulator 50 and the high-pressure side refrigerant before being depressurized by the pressure control valve 30. The refrigerant enthalpy on the inlet side is lowered to improve the refrigeration capacity of the supercritical refrigeration cycle.

  In FIG. 5, the state of the refrigerant in the supercritical refrigeration cycle 1 is shown as a ph (pressure-enthalpy) diagram, and the refrigerant that is the internal fluid flowing through the radiator 20 To a supercritical state.

  Therefore, as shown in FIG. 6 showing the temperature change of the refrigerant in the radiator 20, the refrigerant circulating in the radiator 20 does not change in latent heat (condensation) even if heat is exchanged with the external fluid air to dissipate heat. Not) Changes in sensible heat.

  As shown in FIG. 1, the radiator 20 includes a first core 21 and a second core 22 that form a plurality of core rows in the ventilation direction, a left header tank (for example, a header tank disposed on the left side of the vehicle when mounted) 23, a right It is composed of a header tank (for example, a header tank disposed on the right side of the vehicle when mounted on the vehicle) 24, etc., and each member is made of aluminum or an aluminum alloy and is assembled by fitting, caulking, jig fixing, etc. It is brazed integrally with the provided brazing material.

  The first core 21 disposed on the downstream side of the air flow that is the external fluid (the back side in FIG. 1) is alternately laminated with a plurality of tubes 211 and a plurality of fins 212 (only a part of which is shown) through which the refrigerant flows. Further, side plates 213 and 214 as strength members (reinforcing members) are disposed further outward from the outermost fin 212, and each member is integrally brazed.

  A pair of header tanks (a first header tank 231 and a second header tank 242) extending in the stacking direction of the tubes 211 are provided at the left and right portions of the first core 21 shown in FIG. Is provided.

  The header tanks 231 and 242 are provided with a plurality of tube holes (not shown), and the ends of the tubes 211 are fitted into the tube holes so that the tubes 211 and the header tanks 231 and 242 communicate with each other. It is brazed.

  The second core 22 arranged in parallel with the first core 21 on the upstream side of the air flow (the front side in FIG. 1) has a plurality of tubes 221 and a plurality of fins 222 (only part of which are shown) through which refrigerant flows. The side plates 223 and 224 as strength members (reinforcing members) are disposed on the outer side of the outermost fin 222, and each member is integrally brazed.

  A pair of header tanks (a third header tank 233 and a fourth header tank 244) extending in the stacking direction of the tubes 221 at the left and right portions of the second core 22 shown in FIG. Is provided.

  The header tanks 233 and 244 are provided with a plurality of tube holes (not shown), and the ends of the tubes 221 are fitted into the tube holes so that the tubes 221 and the header tanks 233 and 244 communicate with each other. It is brazed.

  The first header tank 231 and the third header tank 233 are arranged side by side in the air flow direction, and are integrally formed in this example to constitute the left header tank 23 described above.

  Further, the second header tank 242 and the fourth header tank 244 are juxtaposed in the air flow direction, and are integrally formed in this example to constitute the above-described right header tank 24.

  Specifically, the left and right header tanks 23 and 24 are formed by closing both ends of a cylindrical body that is extruded into a shape of a cross section 8.

  A joint block 232 that serves as a refrigerant inlet is brazed to the lower side of the first header tank 231, and a joint block 245 that serves as a refrigerant outlet is brazed to the lower side of the fourth header tank 244. .

  The upper part of the second header tank 242 and the upper part of the third header tank 233 are connected by a conduit 25 made of a cylindrical pipe (round pipe). The inside of the second header tank 242 and the inside of the third header tank 233 are The communication path 25A in the conduit 25 communicates. The conduit | pipe 25 is a piping member in this embodiment.

  As apparent from FIG. 3, the conduit 25 is a straight pipe, and the entire region is disposed between the first core 21 and the second core 22 (between the formation surfaces of both the cores 21, 22), and the communication path 25A is a linear passage.

  Thereby, in the radiator 20, as shown in FIG. 3, the 1st header tank 231, the 1st core 21, the 2nd header tank 242, the conduit | pipe 25 (communication path 25A), the 3rd header tank 233, the 2nd An inverted Z-shaped refrigerant flow path constituted by the core 22 and the fourth header tank 244 is formed.

  Each header tank 231, 242, 233, 244 does not have a partition member or the like formed therein, and is provided in the plurality of tubes 211 of the first core 21 and in the plurality of tubes 221 of the second core 22. The refrigerant flows in the same direction.

  In other words, each of the first core 21 and the second core 22 is a so-called all-path type core (heat exchange unit), and the refrigerant flow direction in the first core 21 and the refrigerant flow direction of the second core 22 Are the same.

  In the above configuration, the high-temperature refrigerant discharged from the compressor 10 flows into the first header tank 231 of the radiator 20 from the joint block 232, and the first header tank 231 and the second header tank 242 are in the first state. When flowing in the tube 211 of the core 21, it is cooled by the air flow after passing through the outside of the second core 22 flowing outside.

  As illustrated in FIG. 3, in the first core 21, the refrigerant is cooled from 150 ° C. to 70 ° C. (changes in sensible heat).

  The refrigerant flowing into the second header tank 242 from the first core 21 flows through the communication path 25A in the conduit 25 and is guided into the third header tank 233, and the third header tank 233 and the fourth header tank 244 are connected to each other. When the air flows in the tube 221 of the second core 22 in the meantime, it is cooled by the air flow flowing outside.

  As illustrated in FIG. 3, in the second core 22, the refrigerant is cooled from 70 ° C. to 50 ° C. (sensible heat change).

  The refrigerant that has flowed into the fourth header tank 244 from the second core 22 is sent from the joint block 232 to the internal heat exchanger 600 side.

  According to the above-described configuration and operation, the so-called all-path orthogonal counter-flow radiator 20 of the present embodiment has the first core 21 and the second core 22 in the direction of the external cooling air flow (external air flow). The refrigerant flows are arranged side by side so that the start sides (upstream side, refrigerant high temperature side) and the end sides (downstream side, refrigerant low temperature side) of the refrigerant flow are adjacent to each other.

  That is, in the first core 21 and the second core 22, the refrigerant flows in the same direction so as to be orthogonal to the cooling air, and the cooling air that has passed through the start end side (the third header tank 233 side) of the second core 22 The cooling air that has passed through the start side (first header tank 231 side) of the first core 21 and passed through the end side (fourth header tank 244 side) of the second core 22 is the end side (second header) of the first core 21. It passes through the tank 242 side.

  Since the refrigerant flows in the same direction in both the cores 21, 22, a temperature difference of the refrigerant in the portion where the first core 21 and the second core 22 are arranged in parallel is formed in the entire area of both the cores 21, 22. can do.

  As a result, the first and second cores 21 and 22 of the all-pass type with a small refrigerant pressure loss can be arranged so that the refrigerant is opposed to the cooling air, and the refrigerant and the cooling air are supplied in the entire area of both the cores 21 and 22. A large temperature difference can be secured. Therefore, the heat exchange efficiency in both the cores 21 and 22 of the radiator 20 can be improved.

  Further, the first header tank 231 on the start end side of the first core 21 and the fourth header tank 244 on the end side of the second core 22 can be separated greatly. Accordingly, it is possible to prevent a decrease in heat exchange performance due to heat transfer between the header tanks 231 and 244.

  In the case of a structure in which the refrigerant is U-turned toward the upstream side of the cooling air flow like a conventional radiator, it is difficult to secure a temperature difference between the refrigerant and the cooling air on the U-turn side of the cores arranged side by side. The heat exchange performance was likely to be lowered due to the heat transfer between the header tanks for introducing and removing the refrigerant.

  In order to suppress this heat transfer, if the header tanks for introducing and introducing the refrigerant are separated from each other in the cooling air flow direction, the size of the radiator tends to increase.

  According to this embodiment, the heat exchange performance can be reliably improved without increasing the size of the radiator 20.

  Further, the first header tank 231 and the third header tank 233 can be integrated, and the second header tank 242 and the fourth header tank 244 can be integrated.

  Thereby, the assembling property of the plurality of cores (the first core 21 and the second core 22) can be improved, and the rigidity can be improved.

  Further, the communication path 25A in the conduit 25 is formed in a straight line. Therefore, the pressure loss of the refrigerant guided from the second header tank 242 to the third header tank 233 can be reduced.

  Further, the entire area of the conduit 25 is disposed between the formation surface of the first core 21 (specifically, the downstream surface of the cooling air) and the formation surface of the second core 22 (specifically, the upstream surface of the cooling air). Has been.

  Therefore, although the communication path 25A that communicates between the second header tank 242 and the third header tank 233 is provided, the size of the radiator 20 is not increased in the flow direction of the cooling air.

(Second Embodiment)
Next, a second embodiment will be described based on FIG.

  The second embodiment is different from the first embodiment in that the number of core arrays is increased. In addition, about the part similar to 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

  As shown in the top view of FIG. 7, in the present embodiment, the radiator 20 includes a first core 21, a second core 22, and a third core 26 that are arranged in parallel in the flow direction of the cooling air.

  Similar to the first and second cores 21, 22, the third core 26 arranged in parallel with the second core 22 on the upstream side of the cooling air flow is configured by laminating a plurality of tubes through which refrigerant flows. A pair of header tanks (fifth header tank 235 and sixth header tank 246) extending in the tube stacking direction are provided at both longitudinal ends of the plurality of tubes.

  The first, third, and fifth header tanks 231, 233, and 235 are juxtaposed in the air flow direction, and are integrally formed in this example to constitute the left header tank 23 </ b> A.

  The second, fourth, and sixth header tanks 242, 244, and 246 are juxtaposed in the air flow direction, and are integrally formed in this example to constitute the right header tank 24A.

  Further, the upper part of the fourth header tank 244 and the upper part of the fifth header tank 235 are connected by a conduit (piping member) 27 similar to the conduit 25, and the inside of the fourth header tank 244 and the fifth header tank 235 are connected. Are communicated by a communication path in the conduit 27.

  According to the above-described configuration, the second and third cores 22 and 26 are the first and second cores referred to in the present invention, and the third, fourth, fifth, and sixth header tanks 233, 244, 235, As the first to fourth header tanks referred to in the present invention as H.246, the present invention is also applied to the refrigerant passage configuration including the second core 22 row and the third core 26 row.

  Therefore, according to the present embodiment, the heat exchange performance of the radiator 20 can be further improved. This is effective when the cooling distance is insufficient with two core rows.

  It should be noted that the application of the present invention is not limited to the number of core rows up to three, and is effective even when applied to one having four or more rows.

(Third embodiment)
Next, a third embodiment will be described based on FIG. 8 and FIG.

  The third embodiment is different from the first embodiment described above in that heat exchange fins are provided in the conduit. In addition, about the part similar to 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

  As shown in a perspective view for explaining distribution in FIG. 8 and a top view in FIG. 9, in this embodiment, fins 251 are provided on the outer periphery of the conduit 25 forming the communication passage 25A. The fins 251 are circular plate fins and are brazed to the outer peripheral surface of the conduit 25.

  According to the above-described configuration, heat exchange between the refrigerant flowing through the communication path 25A in the conduit 25 and the external cooling air can be promoted. Therefore, the heat exchange performance of the radiator 20 can be further improved.

  The heat exchange fins (radiation fins) 251 are not limited to plate fins, and may be, for example, spine fins.

(Fourth embodiment)
Next, a fourth embodiment will be described with reference to FIG.

  The fourth embodiment is different from the first embodiment described above in that the communication path is provided in the side plate. In addition, about the part similar to 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

  As shown in the perspective view for explaining the distribution in FIG. 10, in this embodiment, the communication path 25 </ b> B is provided in the side plate 213 that is the reinforcing member of the first core 21.

  In the present embodiment, a side plate 213 in which two plate members are joined to form a communication path 25B between the plates is employed.

  The refrigerant that has flowed into the second header tank 242 from the first core 21 is guided to the upper space from the partition member 2311 in the first header tank 231 through the communication path 25B formed in the side plate 213, and then this space. And the third header tank 233 through a communication passage 237 that communicates with the third header tank 233.

  According to the above-described configuration, even if it is difficult to provide the conduit 25 as in the first embodiment due to restrictions such as the mounting space of the radiator 20, the second header tank 242 to the third header tank. A refrigerant can be introduced into 233.

  The communication path 25B is not limited to the one formed in the side plate 213 formed by joining a plurality of plate members, and may be one in which the communication path is formed by extrusion molding or the like. In addition, the communication path may be provided in the other side plates 214, 223, and 224.

(Fifth embodiment)
Next, a fifth embodiment will be described with reference to FIG.

  The fifth embodiment is different from the first embodiment described above in that the communication path is provided on a side plate common to a plurality of cores. In addition, about the part similar to 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

  As shown in a perspective view for explaining the flow in FIG. 11, in this embodiment, a communication path 25 </ b> C is provided in a side plate 2131 which is a reinforcing member common to the first core 21 and the second core 22. The communication path 25 </ b> C is formed as a linear path that connects the second header tank 242 and the third header tank 233.

  In the present embodiment, a side plate 2131 is used in which two plate members are joined to form a communication path 25C between the plates.

  According to the above-described configuration, as in the fourth embodiment, even if it is difficult to provide the conduit 25 as in the first embodiment due to restrictions such as the mounting space of the radiator 20, The refrigerant can be introduced from the second header tank 242 to the third header tank 233.

  Further, the communication path 25C in the side plate 2131 is formed in a linear shape. Therefore, the pressure loss of the refrigerant guided from the second header tank 242 to the third header tank 233 can be reduced.

  In addition, since the side plates are common to the plurality of core rows, it is easy to assemble a plurality of rows of cores and to improve the rigidity.

  As in the fourth embodiment, the communication path 25C is not limited to the one formed in the side plate 2131 formed by joining a plurality of plate members.

(Sixth embodiment)
Next, a sixth embodiment will be described with reference to FIG.

  The sixth embodiment is different from the first embodiment in that the communication path is routed upstream of the second core in the cooling air. In addition, about the part similar to 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

  As shown in the perspective view for explaining the flow in FIG. 12, in the present embodiment, the second header tank 242 and the third header tank 233 are connected by a conduit 28 routed from the second core 22 to the windward side. . The second header tank 242 and the third header tank 233 are communicated with each other by a communication passage 25D formed in the conduit 28.

  The conduit 28 includes a straight pipe member 28a and a curved path forming member (elbow member) 28b. The cross-sectional area of the communication path 25D is substantially constant over the communication path direction, and pressure loss in the communication path 25D is suppressed. ing.

  According to the above-described configuration, even if it is difficult to provide the conduit 25 on the outer side in the tube stacking direction of both the cores 21 and 22 due to restrictions such as the mounting space of the radiator 20, the second header tank 242 A refrigerant can be introduced into the third header tank 233.

  Moreover, after producing the first core 21 row and the second core 22 row, respectively, the conduit 28 can be connected and assembled.

(Seventh embodiment)
Next, a seventh embodiment will be described with reference to FIG.

  The seventh embodiment is an example in which the radiator 20 is applied to a heating heat exchanger of a vehicle air conditioner. In addition, about the part similar to 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

  As shown in the perspective view of FIG. 13, in this embodiment, the first and third header tanks 231 and 233 are on the lower side, and the second and fourth header tanks 242 and 244 are on the upper side. The radiator 20 is disposed in an air conditioning case (not shown).

  And when heating a vehicle interior, among the air which passes the 1st, 2nd cores 21 and 22 and blows off from the 1st core 21, it passed the 1st header tank 231 side of the 1st core 21 comparatively high temperature. Is blown out toward the passenger's feet in the passenger compartment, and relatively cool air that has passed near the second header tank 242 of the first core 21 is blown out upward of the passenger in the passenger compartment.

  By distributing the blown air in this manner, it is possible to easily form a head cold foot type temperature distribution in which the blowout temperature is higher on the lower side than on the upper side in the passenger compartment.

(Eighth embodiment)
Next, 8th Embodiment is described based on FIG. 14 and FIG.

  The eighth embodiment is an example in which the radiator 20 is arranged on the cooling air downstream side of the intercooler 90 which is another heat exchanger. In addition, about the part similar to 1st Embodiment, the same code | symbol is attached | subjected and the description is abbreviate | omitted.

  As shown in the perspective view for explaining the distribution in FIG. 14, in the present embodiment, the radiator 20 has the first and third header tanks 231 and 233 on the lower side, and the second and fourth header tanks 242 and 244 on the upper side. The intercooler 90 is disposed on the downstream side of the cooling air flow.

  The core (heat exchanging part) 91 of the intercooler 90 has a dimension in the illustrated vertical direction smaller than the dimension in the illustrated vertical direction of the first and second cores 21 and 22. And the heat radiator 20 is arrange | positioned so that the 3rd header tank 233 may be located immediately after the cooling air flow direction of the intercooler 90. FIG.

  In other words, the intercooler 90 and the radiator 20 are juxtaposed in the cooling air flow direction so that the portion of the second core 22 near the third header tank 233 overlaps the core 91 of the intercooler 90.

  According to the configuration described above, the cooling air that has passed through the core 91 of the intercooler 90 flows into the portion of the second core 22 near the third header tank 233.

  That is, an intercooler is provided at the start end side portion (the portion near the first header tank 231) of the first core 21 and the start end side portion (the portion near the third header tank 233) of the second core 22 where the refrigerant temperature is relatively high. The cooling air heat-exchanged at 90 passes. On the other hand, an intercooler is provided at the end side portion (the portion near the second header tank 242) of the first core 21 and the end side portion (the portion near the fourth header tank 244) of the second core 22 where the refrigerant temperature is relatively low. At 90, cooling air that has not undergone heat exchange passes.

  Therefore, even if the intercooler 90 is arranged on the upstream side of the radiator 20, it is easy to ensure a temperature difference between the cooling air and the refrigerant in the entire area of the first and second cores 21 and 22 of the radiator 20.

  For example, as shown in FIG. 15A, the temperature of the cooling air upstream from the intercooler 90 (front air temperature) is 40 ° C., and the temperature of the cooling air passing through the intercooler 90 is raised to 50 ° C. Even in this case, the respective refrigerant high-temperature portions of the first and second cores 21 and 22 are disposed on the downstream side of the intercooler 90.

  Accordingly, the 50 ° C. cooling air that has passed through the intercooler 90 exchanges heat with a relatively high-temperature refrigerant among the refrigerant in the second core 22, and then a relatively high-temperature refrigerant among the refrigerant in the first core 21. Exchange heat.

  The 40 ° C. cooling air that has not passed through the intercooler 90 exchanges heat with a relatively low-temperature refrigerant among the refrigerant in the second core 22, and then has a relatively low temperature among the refrigerant in the first core 21. Exchange heat with refrigerant.

  Thus, even if the intercooler 90 is disposed on the upstream side of the cooling air of the radiator 20, a relatively large temperature difference between the cooling air and the refrigerant can be secured on the downstream side of the intercooler 90, so that the refrigerant can be effectively used. Can be cooled.

  As shown in FIG. 15 (b), in the case of a configuration in which the refrigerant is U-turned to the upstream side of the conventional cooling air, a temperature difference between the cooling air and the refrigerant is ensured on the U-turn side provided in parallel with the intercooler 90. It is difficult, and the effect of having multiple rows of cores is small.

  In addition, the other heat exchangers arranged in parallel on the upstream side are not limited to the intercooler.

(Other embodiments)
In the first to fifth embodiments, the communication path that connects the second header tank 242 and the third header tank 233 is provided above the first and second cores 21 and 22, and the sixth embodiment In the embodiment, it is provided on the front side of the second core 22, and in the seventh and eighth embodiments, it is provided on the left side in the figure. However, the position of the communication path is not limited to this.

  For example, in the radiators of the first to fifth embodiments, the communication path may be provided on the lower side of both cores, or may be provided on both the upper side and the lower side of both cores. Good. Further, in the radiators of the seventh and eighth embodiments, the communication path may be provided on the right side in the drawing of both cores, or provided on both the left side and the right side in the drawing of both cores. It may be a thing.

  Further, in each of the above embodiments, the refrigerant flow direction of the first core 21 and the refrigerant flow direction of the second core 22 are the same direction, but the relatively high-temperature portion of the refrigerant that changes sensible heat in the first core 21 and As long as the relatively low temperature portions respectively correspond to the relatively high temperature portion and the relatively low temperature portion of the refrigerant that changes in sensible heat in the second core 22, the flow direction of the refrigerant may be slightly different. That is, the refrigerant distribution direction of the first core 21 and the refrigerant distribution direction of the second core 22 may be in substantially the same direction.

  Further, in each of the above embodiments, the header tanks at both ends of the core forming a pair are integrated with a plurality of header tanks corresponding to each core row, but each header tank is a separate body. May be.

  In each of the above embodiments, the refrigerant that has passed all the way through the first core 21 on the downstream side of the cooling air is completely passed in the same direction as the first core 21 on the second core 22 on the upstream side of the cooling air. These structures may be formed by stacking a plurality of stages in parallel with the cooling air flow, and forming a serial refrigerant passage so that the refrigerant flows through each stage sequentially.

  Moreover, although the heat radiator (gas cooler) of each said embodiment was demonstrated as a heat radiator of the refrigeration cycle mounted in a vehicle, it is not limited to this, For example, the heat radiator of a stationary refrigeration cycle may be sufficient.

  In each of the above embodiments, the refrigerant that is the internal fluid is carbon dioxide that has been pressurized to a critical pressure or higher, but may be another supercritical refrigerant.

  Further, the internal fluid is not limited to a fluid in a supercritical state as long as the internal fluid changes in sensible heat. Further, the external fluid is not limited to air.

It is a perspective view showing a schematic structure of radiator 20 which is a heat exchanger in a 1st embodiment to which the present invention is applied. It is a perspective view explaining the distribution direction of the internal fluid and external fluid of radiator 20 in a 1st embodiment. It is a top view explaining the distribution direction of the internal fluid and external fluid of radiator 20 in a 1st embodiment. It is a schematic diagram which shows schematic structure of the supercritical refrigerating cycle 1 provided with the heat radiator 20 of 1st Embodiment. 2 is a ph (pressure-enthalpy) diagram showing a refrigerant state in the supercritical refrigeration cycle 1. FIG. 3 is a graph showing a change in refrigerant temperature in the radiator 20; It is a top view explaining the structure of the heat radiator 20 in 2nd Embodiment, and the distribution | circulation direction of an internal fluid and an external fluid. It is a perspective view explaining the structure of the heat radiator 20 in 3rd Embodiment, and the distribution direction of an internal fluid and an external fluid. It is a top view explaining the structure of the heat radiator 20 in 3rd Embodiment, and the distribution direction of an internal fluid and an external fluid. It is a perspective view explaining the structure of the heat radiator 20 in 4th Embodiment, and the distribution direction of an internal fluid and an external fluid. It is a perspective view explaining the structure of the heat radiator 20 in 5th Embodiment, and the distribution direction of an internal fluid and an external fluid. It is a perspective view explaining the structure of the heat radiator 20 in 6th Embodiment, and the distribution direction of an internal fluid and an external fluid. It is a perspective view explaining the structure of the heat radiator 20 in 7th Embodiment, and the distribution direction of an internal fluid and an external fluid. It is a perspective view explaining the structure of the heat radiator 20 in 8th Embodiment, the distribution direction of an internal fluid, an external fluid, and the positional relationship with another heat exchanger. (A) is a schematic side view explaining the temperature difference between the internal fluid and the external fluid of the radiator 20 in the eighth embodiment, and (b) is the temperature difference between the internal fluid and the external fluid of the conventional radiator. FIG.

Explanation of symbols

20 Heatsink (heat exchanger)
21 1st core 22 2nd core 25, 27, 28 Conduit (piping member)
25A, 25B, 25C, 25D Communication path 90 Intercooler (other heat exchanger)
211, 221 Tube 213, 2131 Side plate (reinforcing member)
231 1st header tank 233 3rd header tank 242 2nd header tank 244 4th header tank 251 Fin (heat exchange fin)

Claims (10)

A plurality of tubes (211) are laminated, and heat exchange is performed between an internal fluid flowing in the same direction in the plurality of tubes (211) and an external fluid flowing outside the plurality of tubes (211), A first core (21) that changes the sensible heat of the internal fluid;
A first header tank (231) connected to a plurality of tubes (211) of the first core (21) on the start end side of the first core (21);
A second header tank (242) connected to a plurality of tubes (211) of the first core (21) on the terminal side of the first core (21);
A plurality of tubes (221) are stacked, arranged in parallel with the first core (21) on the upstream side in the external fluid flow direction, and flow through the plurality of tubes (221) in the same direction. A second core (22) for exchanging heat between the internal fluid after passing through the core (21) and the external fluid flowing outside the plurality of tubes (221) to change the sensible heat of the internal fluid;
A third header tank (233) connected to a plurality of tubes (221) of the second core (22) on the start end side of the second core (22);
A fourth header tank (244) connected to a plurality of tubes (221) of the second core (22) on the terminal side of the second core (22);
A communication path (25A) communicating the second header tank (242) and the third header tank (233);
The heat exchanger, wherein the flow direction of the internal fluid in the first core (21) and the flow direction of the internal fluid in the second core (22) are substantially the same.   The said communicating path (25A) is arrange | positioned in the whole area between the formation surface of the said 1st core (21), and the formation surface of the said 2nd core (22). Heat exchanger.   The piping member (25) connected to the second header tank (242) and the third header tank (233) and forming the communication path (25A) therein is provided. 2. The heat exchanger according to 2.   The heat exchanger according to claim 3, wherein the piping member (25) has heat exchange fins (251) formed on an outer periphery thereof. A reinforcing member (213) for reinforcing at least one of the first core (21) and the second core (22);
The heat exchanger according to claim 1 or 2, wherein the communication path (25B) is formed inside the reinforcing member (213).   The heat exchanger according to any one of claims 1 to 5, wherein the communication path (25A) is formed in a straight line. The external fluid is air;
The external fluid is heated by heat exchange with the internal fluid in the first core (21) and the second core (22) and then blown out into the room. The heat exchanger according to any one of 6.   Out of the external fluid that passes through the first core (21), the external fluid that passes near the first header tank (231) is blown out to the lower side of the room and passes near the second header tank (242). The heat exchanger according to claim 7, wherein an external fluid is blown out upward in the room. The second core (22) is disposed on the downstream side of the other heat exchanger (90) in the flow direction of the external fluid, and part of the second core (22) in the flow direction of the external fluid. (90),
The portion of the second core (22) close to the third header tank (233) is juxtaposed so as to overlap the other heat exchanger (90). The heat exchanger as described in any one.   The heat exchanger according to any one of claims 1 to 9, wherein the internal fluid is a fluid pressurized to a critical pressure or higher.

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