KR100238603B1 - A laminated heat exchanger - Google Patents

Abstract

One end in the stacking direction is provided with an inlet and an outlet of the heat exchange medium, and the inlet is communicated through a communication pipe to a path at the most upstream end away from one end in the stacking direction, and the outlet is one end in the stacking direction at a path at the downstream end. It is in communication. The communication pipe communicates with the hole of the hole means again, and the communication part of the hole means and the communication pipe is provided in the vicinity of the transition part in the first pass of the mating means. In addition, the inlet portion communicates with one path in the stacking direction at one path in front of the most downstream end. The heat exchange medium also flows sufficiently in the tubular element near the downstream side of the partition to suppress nonuniformity in temperature distribution and improve heat exchange efficiency.

Description

Multilayer Heat Exchanger {A LAMINATED HEAT EXCHANGER}

Industrial Applicability The present invention is used for a cooling cycle of a vehicle air conditioner, and the like. A stacked heat exchanger in which pipe elements and fins are alternately stacked in multiple stages, in particular, a pair of tank parts is formed on one side of the pipe element, and an inlet part of the heat exchange medium has a stacking direction. It is related to a laminated heat exchanger of the type installed at one end.

In response to a request for miniaturization of heat exchangers and improvement of heat exchange efficiency, the applicant has developed a heat exchanger having an external shape shown in Fig. 1A, and has conducted various studies on this.

The laminated heat exchanger is stacked in multiple stages through the fins of the tubular elements to form the core body, and a pair of tanks provided on one side of each tubular element is communicated by the U-turn passage part, and the tank portions of the adjacent tubular elements are adapted. In communication with each other, as shown in Fig. 15, a plurality of passes of heat exchange medium flow paths are formed in the core body, and an inlet part 4 and an outlet part 5 of the heat exchange medium are provided at one end in the stacking direction. In the current type, the inlet portion 4 communicates with the communication pipe 20 with respect to the path at the most upstream end, and the outlet portion 5 is directly communicated with the path at the downstream end.

In the heat exchanger described above, when the heat exchange medium flows in from the inlet 4, the heat exchange medium enters the path of the most upstream end through the communication pipe 20, passes through the plurality of paths, and reaches the path of the downstream end of the path. It flows out from the outlet part 5 which communicates with the path | pass of a stage. Here, the heat exchange medium passes through the U-turn passage part twice in a process in which the flow rate in one direction moving from the tank side to the half tank side or from the tank side to the tank side is 1 pass, and the heat exchange medium is from the inlet to the outlet. In the case of a heat exchanger, a four-pass heat exchanger and a three-pass heat exchanger are referred to as a six-pass heat exchanger.

However, since the coolant flows out from one end of the core body, the four-pass stacked heat exchanger has an outlet side (in the lamination direction) when moving from the second pass to the third pass as shown in Fig. 16A. The coolant is ubiquitous in the tubular element near one end side). That is, it is difficult for the refrigerant to flow to the side close to the partition portion α between the first pass and the fourth pass, from the third pass to the fourth pass. It is also proved by the actual measurement data shown as the broken line of FIG. 5A, 5B, or 10A, 10B compared with another part. In addition, in FIG. 5A, 5B or 10A, 10B, a tube number (TUBE No.) is the number of tube elements counted from the one end part which has an entrance part. In addition, the passing air temperature (AIR TEMP.) Refers to the temperature of the heat exchanged between the fins passing through the tube element, and measured at a position 1 to 2 cm away from the downstream end surface of the core body.

Also in the six-pass heat exchanger, as shown in Fig. 16B, the heat exchange medium flows inclined toward the outlet side away from the partition portion α, and as a result, the tube temperature or the passing air in the vicinity of the outlet side of the partition portion α flows. It is estimated that the temperature is different compared to other parts.

Therefore, in this invention, it is a subject to provide the laminated heat exchanger which can improve the heat exchange efficiency by making it flow so that a heat exchange medium may flow to one side so that a heat exchange medium may flow almost uniformly in any pipe element. .

In order to sufficiently flow the heat exchange medium to the tube element near the partition part and to make the temperature distribution of the core body almost uniform, the present inventors actively supply the heat exchange medium to the odd paths separately from the mainstream flow of the heat exchange medium. As a result of finding that the flow can be improved, and earnestly researching the structure of the heat exchanger based on this idea, the present invention has been completed.

That is, the laminated heat exchanger according to the present invention stacks a tube element having a pair of tank portions provided on one side and a U-turn passage portion communicating with the pair of tank portions in multiple stages through pins, and the tank portion of the adjacent tube element. A continuous even-pass heat exchange medium flow path is formed in one pass in the same direction with the flow rate in the same direction of the heat exchange medium, and the inlet and the outlet of the heat exchange medium are provided at one end in the stacking direction, and the inlet is the heat exchange medium. Communicate with the passage at the most upstream end of the flow path through the communication path, and communicate the outlet portion at one end in the stacking direction with the path at the downstream end of the heat exchange medium flow path, and further communicate the communication path with the path at the hole means. And a communication portion between the hole means and the communication path is provided in the vicinity of the transition part of the first means pass. It is.

Here, a stacked heat exchanger having an even-pass heat exchange medium flow path can be imagined as a four- to six-pass heat exchanger, but it can of course also correspond to a heat exchanger having two or more passes or eight passes. The passage means of the hole means through which the communication path communicates refers to, for example, the third stage pass in the four-pass heat exchanger, and one or both of the third stage pass and the fifth stage pass in the six-pass heat exchanger. Point to.

Therefore, in such a configuration, the heat exchange medium flowing from the inlet portion flows into the first stage path of the heat exchange medium flow path through the communication path, and after a plurality of passes, reaches the final stage pass of the heat exchange medium flow path. It flows out of a path through an exit part. At the same time as this flow, the heat exchange medium in the communication pipe directly enters the path of the hole means, and then flows through the downstream path to reach the path of the final stage and flows out from the path of the final stage through the outlet.

The heat exchanging medium which transitions from the mating path to the hole-passing path is formed in correspondence with the forces sent from the mating-pass path in addition to the fact that the outlet part and the downstreammost path communicate at one end in the stacking direction. Try to flow away from a partition. However, since the communication path communicates with the passage of the hole means, and furthermore, this communication portion is provided near the transition part in the first pass of the mating means, in any case, the pipe element which easily reduces the refrigerant flow rate (the hole means of the hole means). The heat exchange medium flows sufficiently in the same way as the other pipe elements in the pipe element near the transition part from one of the pipe elements constituting the path, thereby causing a large bias in the temperature distribution to be represented as a solid line in FIGS. 5A and 5B. This is eliminated, and the above problem can be justified.

In addition, in order to achieve a uniform temperature distribution of the core body, a tube element having a pair of tank portions provided on one side and a U-turn passage portion communicating with the pair of tank portions is laminated in multiple stages through pins. The tank portion is in proper communication with each other to form a continuous even pass heat exchange medium flow path having the same flow velocity in the same direction of the heat exchange medium as one pass, and having an inlet and an outlet of the heat exchange medium at one end in the stacking direction. And communicate with the outlet portion at the one end in the stacking direction at the downstream end of the heat exchange medium flow path by communicating with the communicating pipe through a communication pipe at the most upstream end of the heat exchange medium flow path. The heat exchanger may be configured to communicate with one pass in front of the pass at one end in the stacking direction. In such a configuration, the heat exchange medium introduced from the inlet portion flows into the uppermost path of the heat exchange medium flow path through the communication pipe, and after passing a plurality of passes, reaches the path of the lowest downstream end of the heat exchange medium flow path. It exits through the exit in the pass. At the same time, the heat exchange medium of the inlet part flows in at one end in the stacking direction to a pass before one of the paths at the downstream end, and then flows a downstream path to reach the path at the downstream end and exits at this downstream path. Outflow through wealth.

For this reason, the heat exchange medium sent by the even numbered path in front of the pass of the lowermost stage collides with the heat exchange medium which flows in directly from the inlet, and almost passes to the pipe element constituting this path. Evenly distributed, and thus, in a four-pass heat exchanger, as shown by the solid lines in FIGS. 10A and 10B, large deviation in temperature distribution is eliminated.

In the case where the number of passes is large, such as a heat exchanger having six or more passes, or when the number of pipe elements per one pass is large, such as a three-pass heat exchanger, the heat exchange medium may be used even when the inlet portion is connected to one of the paths in the lowermost stage. To think of things that are causing the bias. However, in such a case, the above-described configuration in which the communication path communicates with the path of the hole means and arranges the communication path of the hole means and the communication path in the vicinity of the transition part from the path of the first partner means is used in combination. By responding.

EMBODIMENT OF THE INVENTION Hereinafter, embodiment of this invention is described by drawing. 1 and 2, the laminated heat exchanger 1 alternately stacks the fins 2 and the tubular elements 3 to form a core body, and at one end in the lamination direction of the tubular elements 3, a heat exchange medium. For example, the inlet part 4 and the outlet part 5 are provided, for example, the 4-pass type evaporator, The tube element 3 is the tube element 3a, 3b of the both ends of a stacking direction, and the tube element which has the expansion tank part mentioned later ( 3c, 3d) and the tube element 3e in the center thereof are removed, and two molding plates 6a shown in Fig. 3 are joined together.

The forming plate 6a is formed by pressing a plate made of aluminum, and at the one end, two bulging portions 7 and 7 for forming rice bowls are formed at one end thereof, and the passage is formed continuously. The bulging part 8 is formed, The recessed part 9 for attaching the communication pipe mentioned later is formed between the bulging parts for tank formation, and the two tank formation bulge is formed in the swelling part 8 for passage formation. A protrusion 10 extending between the exit portions 7 and 7 to the vicinity of the free end of the forming plate 6a is formed. In addition, 11 is a circular bead formed on the forming plate in order to increase the heat exchange efficiency, and each bead 11 is joined to the bead formed on the opposing portion when two forming plates are joined. .

The tank-forming bulge 7 is swelled larger than the passage-forming bulge 8, and the protrusions 10 are formed to be flush with the bonding material at the edge of the molding plate, and the two forming plates 6a are formed. When the joints are joined at their edges, the protrusions 10 are also joined to each other to form a pair of tank portions 12 and 12 by opposing tank-forming bulging portions 7, and at the same time, opposing passage-forming swelling portions. The U-turn passage part 13 which connects between tank parts is formed by (8).

The tubular elements 3a and 3b at both ends of the stacking direction are formed by joining the flat plate 15 to the outer side of the forming plate 6a of FIG. In addition, the tubular elements 3c and 3d are formed with a tank part 12 having the same size as the tubular element 3 and the tank parts 12a and 12b enlarged to fill the recesses. The double tube element 3c is constituted by assembling the forming plates 6b and 6c shown in Figs. 4A and 4B, and each forming plate 6b and 6c has one tank forming bulge 7a and 7b on the other side. The through hole 14 for inserting and joining the communication pipe 20 mentioned later is formed in the tank formation swelling part 7a which is extended and formed so that the tank formation swelling part 7 of the tank may be enlarged, and the enlarged formation of the shaping | molding plate 6b is carried out. It is. On the other hand, the tubular element 3d is constructed by assembling the forming plate 6b of FIG. 4A and the forming plate symmetrically, for example, and the communicating pipe 20 is joined by inserting the through hole 14. . In the other configuration of the forming plates 6b and 6c, that is, the passage forming swelling portion 8 is formed next to the swelling portion for forming the tank, and near the free end of the forming plate between the swelling portion for forming the tank 7. The lighting in which the protrusions 10 are formed over the same is the same as that of the forming plate 6a shown in FIG.

1 and 2, the heat exchanger 1 includes the first and second two tank groups 16 in which adjacent elements are joined to each other in the tank unit and are joined in the stacking direction (perpendicular to the ventilation direction). , 17), and one tank group 16 including an enlarged tank portion 12a is provided on the tank-forming bulge portion 7 from which the molding plate 6e, which is located substantially at the center of the stacking direction, is removed. Each tank part communicates through the formed through hole 18, and all the tank parts communicate with the other tank group 17 through the through hole 18 without being blocked.

Here, the tubular element 3e has the same appearance as the forming plate 6a shown in Fig. 3, and is formed by assembling a forming plate 6e in which one of the tank forming bulging portions is not provided with a through hole. The partition part 19 which has a cylinder part and closes one tank group 16 is formed. The partition 19 may be configured to close the through-hole by sandwiching a thin plate between the tubular element 3e and the tubular element adjacent to the tubular element 3e instead of closing the bulge for tank formation.

Accordingly, the partition 19 allows the first tank group 16 to communicate with the first tank block 21 including the expansion tank 12a and the second tank block 22 in communication with the outlet 5. The 2nd tank group 17 which is divided into and is not partitioned comprises the 3rd tank block 23. As shown in FIG. In addition, in this embodiment, the tube element 3d in the 11th stage and the tube element 3e in the 14th stage are counted from the right end (the end provided with the inlet part 4 and the outlet part 5) in the figure, The tubular element 3c is arrange | positioned at the 22nd stage, respectively.

Thus, the inlet portion 4 and the outlet portion 5 provided at one end in the stacking direction are formed by joining the entrance passage forming plate 24 to the flat plate 15 of the tubular element 3a. The inlet passage 25 and the outlet passage 26 are formed between the plates in the middle of the rectangular direction of the flat plate 15 over the tank portion side.

The inlet 28 and the outlet 29 are respectively installed in the upper part of the inlet passage 25 and the outlet passage 26 through the lever 27 fixing the expansion valve, and the inlet passage 25 and the enlarged tank portion 12a. ) Is communicated with the communication passage formed by the communication pipe 20 fixed to the recess (9), the second tank block 22 and the outlet passage 26 in the hole formed in the plate (15) Communicating through.

Moreover, the communication pipe 20 attached to the recessed part 9 is attached by inserting through the through-hole 14 of each forming plate which comprises the pipe element 3d, and the clearance gap is formed between the through-hole 14. The main wall hole is formed in the part inserted in the tank part 12b without being sealed, and a refrigerant | coolant flows out into the tank part 12b.

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 shows a stacked heat exchanger according to the present invention, in which Fig. 1A is a view showing a cross section perpendicular to the ventilation direction, and Fig. 1B is a view showing a side surface provided with an inlet and an outlet.

FIG. 2A is a bottom view of a four-pass stacked heat exchanger according to FIG. 1, and FIG. 2B is a conceptual diagram illustrating a flow of a heat exchange medium of the stacked heat exchanger according to FIG. 1.

FIG. 3 is a view showing the most commonly used shape plate of the laminated heat exchanger according to FIG. 1. FIG.

Fig. 4 shows a forming plate used as a tubular element having an enlarged tank portion, and Fig. 4A shows a forming plate having an enlarged tank forming bulge without forming a through hole for inserting a communication pipe.

FIG. 5 is a view showing the blown air temperature when the stacked heat exchanger according to FIG. 1 is used. FIG.

Fig. 5A is a characteristic diagram showing the temperature of air passing through the top of the stacked heat exchanger (representative temperature of the air passing through the upper half of the tubular elements), and Fig. 5B is the temperature of air passing through the bottom of the stacked heat exchanger (tubular elements). Characteristic curve of air passing through the lower half of the liver).

FIG. 6A is a bottom view of the six-pass immersion heat exchanger, and shows a configuration in which the laminated heat exchange medium is introduced into the first and third passes, and FIG. 6B shows the flow of the heat exchange medium of the six-pass laminated heat exchanger. Conceptual diagram.

FIG. 7A is a bottom view of a six-pass stacked heat exchanger, and shows a configuration when the heat exchange medium flows into the first, third, and fifth passes, and FIG. 7B shows the heat exchange medium of the six-pass stacked heat exchanger. Conceptual diagram showing the flow of flow.

FIG. 8 is a view showing another embodiment of the stacked heat exchanger according to the present invention, and FIG. 8A is a view showing a cross section perpendicular to the ventilation direction, and FIG. 8B is a view showing a side surface at which an inlet and an outlet are provided.

FIG. 9A is a bottom view of the four-pass stacked heat exchanger of FIG. 8, and FIG. 9B is a conceptual diagram illustrating a flow of a heat exchange medium of the stacked heat exchanger of FIG. 8.

FIG. 10 shows the blowing air temperature when the stacked heat exchanger according to FIG. 8 is used, and FIG. 10A shows the temperature of the air passing through the top of the stacked heat exchanger (representative temperature of the air passing through the upper half of the tubular elements). Fig. 10B is a characteristic diagram showing the temperature of air passing through the bottom of the laminated heat exchanger (representative temperature of air passing through the lower half of the tube elements).

FIG. 11A is a schematic diagram of a six-pass stacked heat exchanger in which a heat exchange medium flows into a first pass through a communication pipe at the inlet, and a heat exchange medium directly flows into a fifth pass, and FIG. Conceptual diagram showing the flow of heat exchange medium in a pass type stacked heat exchanger.

12A shows a bottom of a six-pass stack type heat exchanger that directly introduces a heat exchange medium from the inlet to the fifth pass and simultaneously introduces the heat exchange medium through the communication pipe in the first and third passes, and FIG. Conceptual diagram showing the flow of heat exchange medium in a six-pass stacked heat exchanger.

FIG. 13A is a bottom view of a two-pass stacked heat exchanger in which a heat exchange medium is introduced into a first pass through a communication pipe at the inlet and directly enters the heat exchange medium through a small hole, and FIG. 13B is a two pass view. Conceptual diagram showing the flow of a heat exchange medium of a stacked heat exchanger.

FIG. 14A is a bottom view of a two-pass stacked heat exchanger in which a heat exchange medium flows directly from the inlet to the first pass and simultaneously introduces a heat exchange medium from the end and the middle of the communication pipe into the first pass, and FIG. Conceptual diagram showing the flow of heat exchange medium in a 2-pass type stack heat exchanger.

15 is a perspective view illustrating a flow of a heat exchange medium of a conventional 4-pass type heat exchanger.

FIG. 16A is a conceptual diagram illustrating the flow of the heat exchange medium of the stacked heat exchanger according to FIG. 15, and FIG. 16B is a conceptual diagram illustrating the flow of the heat exchange medium of the six-pass stacked heat exchanger.

* Explanation of symbols for main parts of the drawings

1: stacked heat exchanger 2: fin

3: tube element 4: inlet part

5: outlet part 6a: forming plate

7 swelling part for forming 8 swelling part for passage formation

9: recess 10: protrusion

11: Bead 12, 13: Tank

14: through air 16, 17: tank group

18: through-hole 19: partition part

20: communication pipe 21: tank block

23: 3rd tank 25: entrance passage

26: outlet passage 28: inlet

29: outlet 30, 31: partition part

32: 1st tank block 35: 4th tank block

36: pore

In the above configuration, the refrigerant introduced from the inlet portion 4 enters the expansion tank portion 12a through the communication pipe 20, is injected into the entire first tank block 21, and the first tank block ( The U-turn passage part 13 of the tubular element corresponding to 21 is raised along the protrusion 10 (first pass). Then, U turns above the ledge 10 to descend (second pass), and the tank group on the opposite side (third tank block 23) is reached. Then, it moves parallel to the remaining tubular element which comprises the 3rd tank block 23, and raises the U-turn passage part 13 of the tubular element again along the protrusion 10 (3rd pass). Then, the U-turn above the protrusion 10 is lowered (fourth pass), guided to the tank portion constituting the second tank block 22, and then flows out of the outlet portion 5 after the opening.

Regarding this mainstream flow, the refrigerant guided into the communication pipe 20 enters the third tank block 23 at the enlarged tank portion 12b of the tubular element 3d through the sidewall hole, The U-turn passage portion 13 of the tubular element constituting the third pass flows while joining the flow of mainstream sent from the two passes, and flows out of the outlet portion 5 after the opening.

At this time, since the outlet portion 5 is connected to the second tank block 22 through the stacking direction end portion of the core body, the refrigerant shifting from the second pass to the third pass is a pipe close to the one outlet portion. Although the element may be biased, the communication pipe 20 communicates with the third pass in the vicinity of the transition part in the second pass, so that the tubular element near the partition 19 among the tubular elements constituting the third and fourth passes. Even the refrigerant flows sufficiently. As shown by the solid lines in Figs. 5A and 5B, the flow of air passing through the exit side of the partition portion 19 (especially TUBE No. 7-13) is lower than that of the conventional heat exchanger, and as a result, the overall average It is also proven to have a temperature distribution.

6 and 7 show the configuration in which the above technical concept is used for a six-pass heat exchanger. 6 shows an example in which the tubular element 26 is laminated, and counts from the end where the inlet portion 4 and the outlet portion 5 are installed, and the tubular element having no through-holes in the ninth and seventeenth stages ( 3e) is arrange | positioned, and the partition part 30 which divides the 1st tank group 16 by the ninth-stage tube element 3e is comprised, and the 2nd is by the 17th-stage tube element 3e. The partition part 31 which partitions the tank group 17 is comprised. Further, the tubular element 3d is arranged at the fifteenth stage and the tubular element 3c is arranged at the twenty-third stage. In the tubular element 3c, the tank part 12a on the side of the second tank group 17 is enlarged. In the pipe element 3d, the tank part 12b on the side of the first tank group 16 is enlarged. Corresponding to this configuration, the position of the circumferential wall hole of the communication pipe 20 is also formed in accordance with the position of the pipe element 3d.

Accordingly, the first tank group 16 is connected to the first tank block 32 including the enlarged tank portion 12b by the partition portion 30 and the second tank block 33 communicating with the outlet portion 5. The second tank group 17 is divided by the partition portion 31 into a third tank block 34 including the enlarged tank portion 12a and a fourth tank block 35 other than that.

In such a configuration, the refrigerant flowing in from the inlet portion 4 is dispersed throughout the third tank block 34 through the communication pipe 20, and the U turn of the tubular element corresponding to the third tank block 34. It reaches the tank group (1st tank block 32) of an opposite side through the passage part 13 (1st, 2nd path). It is then moved in parallel to the remaining tubular element constituting the first tank block 32 and guided to the tank portion constituting the fourth tank block 35 through the U-turn passage part 13 of the tubular element (first 3, 4th pass), and further, the tank portion to move to the rest of the tubular elements constituting the fourth tank block 35, passing through the U-turn passage part 13 again to form the second tank block 33 (5th and 6th pass), and after that, it exits the outlet 5. At the same time as the mainstream flow, the refrigerant introduced into the communication pipe 20 flows into the first tank block 32 through the enlarged tank portion 12b of the tubular element 3d, and the mainstream is sent in the second pass. While joining with the flow of the main flow, the flow path flows out of the outlet part 5 by passing the path of the third pass or less.

Thus, since the communication pipe 20 is connected to the 3rd path near the transition part from a 2nd path, the refrigerant | coolant is sufficient also in the tubular element which is close to the partition 31 among the tubular elements which comprise 3rd and 4th path | pass. By flowing, at least the temperature distribution of the central portion of the core body can be made smoother than that of the conventional heat exchanger. Therefore, in the heat exchanger of the six pass, it is apparent that the flow of the refrigerant in the third and fourth passes is improved, but in the flow of the fifth and sixth passes, the refrigerant is biased toward the outlet. In order to cope with this, in the heat exchanger shown in Fig. 7, the coolant flows directly into the fifth pass in the vicinity of the transition part from the fourth pass. That is, the tubular element 3d which makes the tank part 12b extended in the 7th step | paragraph of the heat exchanger shown in FIG. 6 the 2nd tank group 17 side is arrange | positioned, and this tank part 12b of this 7th end side is arrange | positioned. A circumferential wall hole opening in the tank portion is formed in the communication pipe 20 to be inserted.

In such a configuration, as shown in FIG. 7B, the coolant sufficiently flows in the tubular element not only near the downstream of the partition part 31 but also in the downstream vicinity of the partition part 30, and the coolant is injected almost equally to all the tubular elements. The temperature of the air passing through the heat exchanger can be further smoothed.

In FIG.8 and FIG.9, another embodiment of this invention shows, and mainly demonstrates the different part below, and attaches | subjects the same code | symbol to the same part, and abbreviate | omits description in the part shown in the figure.

This laminated heat exchanger is a four-pass heat exchanger as shown in Figs. 1 and 2, and the communication pipe 20 is used only for communicating the inlet portion 4 with the expansion tank portion 12a of the tubular element 3c. An inlet passage 25 constituting the inlet portion 4 is enlarged in a direction away from the outlet passage 26 and passes through the small hole 36 formed in the plate-like plate 15, one pass in front of the downstreammost stage, that is, It is the structure connected also to the 3rd step | pass. This small hole 36 is formed smaller than the diameter of the communication pipe 20, and a large amount of refrigerant is prevented from flowing into the third pass from the inlet portion 4.

In such a configuration, the refrigerant flowing from the inlet portion 4 passes through the communication pipe 20 to enter the expansion tank portion 12a and is dispersed throughout the first tank block 21, and the first tank block 21. The U-turn passage portion 13 of the tubular element corresponding to) rises along the protrusion 10 (first pass). Then, the U-turn above the protrusion 10 is lowered (second pass), and the tank group on the opposite side (the third tank block 23) is reached. Then, it moves in parallel to the rest of the tubular elements constituting the third tank block 23, and ascends the U-turn passage part 13 of the tubular element again along the protrusion 10 (third pass). And the U turn above the doljo 10 to descend (fourth pass). It is led to the tank part which comprises the 2nd tank block 22, and flows out from the outlet part 5 after opening.

With respect to the flow of the mainstream, the refrigerant at the inlet 4 enters the second tank block 23 through the small holes 36 and joins with the flow of the mainstream sent from the second pass to form the third pass. U-turn passage portion 13 of the rise along the protrusion (10). Thus, the U-turn above the ledge 10 is lowered (fourth pass), and flows out of the outlet 5 after that.

Therefore, in the tank group constituting the third pass of the third tank block, the refrigerant sent in the second pass and the refrigerant flowing in the inlet 4 are concentrated, and the refrigerant sent in the second pass further includes the inlet 4. The impingement flows toward the outlet by colliding in the direction opposite to the refrigerant flowing in the cavity), and the refrigerant flows sufficiently in the tubular element near the outlet side of the partition 19 among the tubular elements forming the third and fourth passes. As a result, as shown by the solid lines in FIGS. 10A and 10B, the air temperature passing between the tubular elements (particularly tubes No. 7 to 13) near the outlet side of the partition portion 19 is lower than that of the conventional heat exchanger. Overall averaged temperature distribution.

11 to 14 show another form of the heat exchanger that forms the same small holes 36 at the end of the core body at the end of the core body, and FIGS. 11 and 12 show a heat exchanger having a six-pass heat exchanger as shown in FIGS. 14 denotes two heat exchangers, respectively.

In the heat exchanger illustrated in FIG. 11, the inlet portion 4 communicates with one of the paths in the lowermost stage, that is, the fifth stage, so that the refrigerant flowing into the inlet portion 4 communicates with the communication pipe 20. After passing through the first tank block 32 through a plurality of passes through the outlet portion 5, and flows directly from the fourth pass through the small hole 36, and flows out of the fourth pass It collides with the refrigerant and diffuses through all of the tubular elements constituting the fifth pass and passes through the U-turn passage. For this reason, the refrigerant | coolant flows enough also in the tubular element of the downstream vicinity of the partition part 30 among the tubular elements which comprise the 5th and 6th path | passes, and it can improve temperature distribution.

In the above configuration, the flow of at least the fifth and sixth passes can be improved, and the temperature distribution can be improved in the limit. However, in the third and fourth passes, the refrigerant is biased downstream. Becomes For this reason, in the heat exchanger shown in FIG. 12, the inlet part 4 and the 5th path | pass directly communicate with the heat exchanger shown in FIG. 6 by the small hole 36. As shown in FIG. This structure makes it possible to obtain a temperature distribution in which not only the fifth and sixth passes but also the third and fourth passes are dispersed almost uniformly and are not biased as a whole.

In addition, the two-pass heat exchanger shown in FIG. 13 is laminated at the 27 end, and the inlet part 4 is connected to the enlarged tank part of the 22nd-stage pipe element 3c via the communication pipe 20, The inlet part 4 communicates with the path | pass in front of one of the path | lowest stages, ie, the path | pass of a 1st stage, through the small hole 36. As shown in FIG. Accordingly, the refrigerant introduced from the inlet 4 enters the second tank group 17 through the communication pipe 20, and simultaneously enters the second tank group through the small holes 36 and collides with each other to join. It passes through the U-turn passage of each pipe element, and flows out from the first tank group 16 to the outlet portion 5. Even in such a configuration, the refrigerant flowing into the second tank group 17 in the communication pipe 20 and flowing into the second tank group in the small holes 36 by appropriately adjusting the size of the small holes 36. Since the flow with the refrigerant can be controlled, a nearly uniform temperature distribution can be obtained by dispersing the refrigerant almost uniformly as a whole.

In particular, in a two-pass heat exchanger, it is expected that it is difficult to uniformly disperse the refrigerant in all the tube elements because the number of tube elements per one pass increases. In this case, as shown in FIG. It is effective to arrange the tubular element 3d having the 12b and to introduce the refrigerant into the second tank group 17 in the middle of the communication pipe 20.

As described above, according to the present invention, in the heat exchanger having the entrance and exit portion of the heat exchange medium at one end in the stacking direction of the core body, since the active heat exchange medium is introduced into the vicinity of the transition portion from the passage of the hole means, the downstream of the partition portion The heat exchange medium can also flow sufficiently in the tube element near the side, and thus, the drift of the heat exchange medium can be suppressed, the temperature distribution of the heat exchanger can be improved, and the shape of heat exchange efficiency can be achieved.

In the conventional heat exchanger in which the heat exchange medium is drift, the passage resistance is increased because the heat exchange medium flows intensively in a predetermined pipe element, but according to the present invention, the heat exchange medium flows almost uniformly in each pipe element. As a result, passage resistance can be reduced.

Claims (6)

Each of the two forming plates 6a, 6b, and 6c has a pair of tank portions 12 formed at one end in the longitudinal direction, a path for communicating with one of the pair of tank portions 12, and the pair of tank portions. A plurality of tubular elements 3a, 3b, 3c having a return passage portion 13 having a return passage communicating with the other side; Fins 2 alternately stacked with the tubular elements 3a, 3b, 3c; An inlet passage 25 communicating with the heat exchange medium inlet 4 and an outlet communicating with the exchange medium outlet 5, installed on one side of the pipe element 3a, 3b, 3c and the stacking direction of the fin 2; Passage 26; A pair of tank groups 16 and 17 constituted by a pair of tank portions 12 continuous in the stacking direction; A first pass portion constituted by one tank portion 12 constituting one of the tank groups 16 and 17 and a return path of the return passage portion 13 communicating with the tank portion; A second path portion constituted by the other tank portion 12 constituting the other side of the tank group 16, 17, and a return path of the return passage portion 13 communicating with the tank portion 12; A communication pipe constituting the first pass portion and communicating at least one enlarged tank portion 12a and the inlet passage 25 and the enlarged tank portion 12a which extend from one tank portion to the other tank portion side. (20), wherein the tank part (12) located at one end of the first pass part in the stacking direction is in direct communication with the inlet passage (25). 2. The expansion tank portion 12a is a tank portion constituting the first pass portion, and has an approximate center of the tank portion 12 constituting the first pass portion and an end portion of the other side in the stacking direction. Stacked heat exchanger, characterized in that the tank portion located between. The said expansion tank part 12a is a tank part located between the substantially center part of the tank part which comprises the said 1st path part, and the edge part of the other side of the said stacking direction, and the said 1st path part. Laminated heat exchanger, characterized in that one tank located between the approximately center of the tank portion to constitute and one end of the stacking direction. The small hole 36 which communicates between the inlet passage 25 and the tank part 12 located in the lamination direction one end side of the said 1st path part is larger than the diameter of the said communication pipe 20. Stacked heat exchanger, characterized in that small. The small hole 36 which communicates between the inlet passage 25 and the tank part 12 located in the lamination direction one end side of the said 1st path part is larger than the diameter of the said communication pipe 20. Stacked heat exchanger, characterized in that small. The small hole 36 which communicates between the inlet passage 25 and the tank part 12 located in the lamination direction one end side of the said 1st path part is larger than the diameter of the said communication pipe 20. Stacked heat exchanger, characterized in that small.