JP2005308386A - Heat exchanger - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a heat exchanger with excellent heat exchanging performance. <P>SOLUTION: This heat exchanger 1 comprises a heat exchanging core part 4 constituted by arranging two rows of groups 13 of heat exchanging tubes made by a plurality of heat exchanging tubes 12 in the air flow direction, a refrigerant inlet header part 5 arranged on the upper end side of the heat exchanging tubes 12 and to which the heat exchanging tubes 12 of one row of the groups 13 of the heat exchanging tubes are connected, and a refrigerant header part 6 arranged on the rear side of the refrigerant inlet header part 5 on the upper end side of the heat exchanging tubes 12 and to which the heat exchanging tubes 12 of one row of the groups 13 of the heat exchanging tubes are connected. A refrigerant inlet 37 is formed on a cap 19 blocking one opening of the refrigerant inlet header part 5. A guide 40 inclining upward toward inside of the refrigerant inlet header part 5 is provided to the lower side edge part of the refrigerant inlet 37 of the cap 19. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a heat exchanger, and more particularly to a heat exchanger used as an evaporator of a car air conditioner that is a refrigeration cycle mounted on an automobile, for example.

  In this specification and claims, the term “aluminum” includes aluminum alloys in addition to pure aluminum. Further, in this specification and claims, the downstream side in the ventilation direction (the direction indicated by the arrow X in FIG. 1) is referred to as the front, and the opposite side is referred to as the rear. And

  Conventionally, as a evaporator for a car air conditioner, a plurality of flat hollow bodies formed by brazing peripheral edges with a pair of plate-shaped plates facing each other are arranged in parallel, and a corrugated fin with a louver between adjacent flat hollow bodies A so-called laminated evaporator, in which the above is disposed and brazed to a flat hollow body, has been widely used. However, in recent years, there has been a demand for further reduction in size and weight and performance of the evaporator.

  As an evaporator satisfying such a requirement, the present applicant firstly arranged two rows of heat exchange tube groups, each of which is composed of a plurality of heat exchange tubes arranged at intervals, arranged in the ventilation direction. It is provided with a configured heat exchange core part, a refrigerant inlet / outlet tank arranged on the upper end side of the heat exchange core part, and a refrigerant turn tank arranged on the lower end side of the heat exchange core part. The inside of the tank is partitioned into a refrigerant inlet header portion and a refrigerant outlet header portion arranged in a ventilation direction by a partition wall, and a refrigerant inlet is formed at one end of the refrigerant inlet header portion, and is the same as the refrigerant inlet in the refrigerant outlet header portion A refrigerant outlet is formed at the end, and the refrigerant turn tank is partitioned into a refrigerant inflow header portion and a refrigerant outflow header portion arranged in the ventilation direction by a partition wall, and is spaced in the length direction from the refrigerant turn tank partition wall The A plurality of refrigerant passage holes are formed, the upper end of the heat exchange pipe of the front heat exchange pipe group is the refrigerant inlet header part, and the upper end of the heat exchange pipe of the rear heat exchange pipe group is the refrigerant outlet header part. The lower end of the heat exchange tube of the front heat exchange tube group is connected to the refrigerant inflow header portion, and the lower end of the heat exchange tube of the rear heat exchange tube group is connected to the refrigerant outflow header portion. The refrigerant that is connected to each other and flows into the refrigerant inlet header of the refrigerant inlet / outlet tank flows into the refrigerant inflow header of the refrigerant turn tank through the heat exchange pipe of the front heat exchange pipe group, and then the refrigerant in the partition wall Proposed an evaporator that flows into the refrigerant outflow header through the passage hole, and further flows into the refrigerant outlet header of the refrigerant inlet / outlet tank through the heat exchange pipe of the rear heat exchange pipe group ( Patent Document 1).

  However, as a result of various studies by the present inventors, in the evaporator described in Patent Document 1, the refrigerant inlet of the refrigerant inlet header and the refrigerant outlet of the refrigerant outlet header are formed at the same end of the refrigerant inlet / outlet tank. Further, it has been found that the following problem may occur due to the fact that the upper end portion of the heat exchange tube is connected in a state of protruding into the refrigerant inlet header portion.

That is, the portion of the heat exchange pipe that protrudes into the refrigerant inlet header portion becomes a resistance against the refrigerant flowing in from the refrigerant inlet, so that the refrigerant flowing into the refrigerant inlet header portion hardly flows to a position far from the refrigerant inlet. Therefore, a large amount of refrigerant flows into the heat exchange pipe located near the refrigerant inlet in the front side heat exchange pipe group and the refrigerant flow rate increases, and a small amount of refrigerant flows into the heat exchange pipe located far from the refrigerant inlet. As a result, the refrigerant flow rate is reduced, and the refrigerant flow in the heat exchange pipe located near the refrigerant inlet in the rear heat exchange pipe group is increased, and the refrigerant in the heat exchange pipe located far from the refrigerant inlet is used. The flow rate is reduced. As a result, the amount of refrigerant that contributes to heat exchange becomes non-uniform in the length direction of the refrigerant inlet / outlet tank in the heat exchange core, and the temperature of the air that has passed through the heat exchange core also becomes non-uniform depending on the location. It has been found that the effect of improving the heat exchange performance of the evaporator cannot be obtained sufficiently. Such a problem occurs particularly remarkably when the flow rate of the refrigerant is small.
Japanese Patent Laid-Open No. 2003-75024

  An object of the present invention is to solve the above problems and provide a heat exchanger having excellent heat exchange performance.

  In order to solve the above-mentioned problems, the present invention comprises the following aspects.

1) It has a refrigerant inlet header part and a refrigerant outlet header part arranged side by side in the front-rear direction at the upper end part, and a refrigerant circulation path passing through both header parts, and a refrigerant inlet is formed at one end of the refrigerant inlet header part. In addition, a refrigerant outlet is formed at the same end as the refrigerant inlet in the refrigerant outlet header, and the refrigerant flowing into the refrigerant inlet header from the refrigerant inlet returns to the refrigerant outlet header through the refrigerant circulation path and is sent out from the refrigerant outlet. In the heat exchanger that is supposed to be
The refrigerant inlet is formed in a closing member that closes one end opening of the refrigerant inlet header portion, and a guide that is inclined upward toward the inside of the refrigerant inlet header portion is provided at a lower edge of the refrigerant inlet in the closing member. Exchanger.

  2) The heat exchanger according to 1) above, wherein the guide is a partial spherical body.

  3) The heat exchanger according to 1) or 2) above, wherein the refrigerant inlet of the refrigerant inlet header is circular and the inner diameter thereof is 3 to 8.5 mm.

  4) The heat exchanger according to any one of 1) to 3), wherein the protruding end surface of the guide is located on an inclined surface inclined with respect to the vertical inner surface of the closing member.

  5) The heat exchanger according to 4) above, wherein an inclined angle between the inclined surface on which the protruding end surface of the guide is located and the vertical inner surface of the closing member is 15 to 60 degrees.

  6) The closing member has a first closing portion that closes one end opening of the refrigerant inlet header portion, and a second closing portion that closes an opening at the same end as the refrigerant inlet in the refrigerant outlet header portion, The heat exchanger according to any one of 1) to 5) above, wherein a refrigerant inlet is formed in the closed portion and a guide is provided, and a refrigerant outlet is formed in the second closed portion.

  7) A joint plate having a refrigerant inlet leading to the refrigerant inlet of the closing member is joined to one end of the refrigerant inlet header, and the refrigerant inlet of the refrigerant inlet header is eccentric above the refrigerant inlet of the joint plate. The heat exchanger according to any one of 1) to 6) above.

  8) The heat exchanger according to 7) above, wherein the amount of eccentricity of the refrigerant inlet of the refrigerant inlet header portion with respect to the refrigerant inlet of the joint plate is 0.5 to 3 mm.

  9) The joint plate is joined across the refrigerant inlet header and the refrigerant outlet header, and the joint plate is formed with a refrigerant outlet leading to the refrigerant outlet in addition to the refrigerant inlet leading to the refrigerant inlet 7) Or the heat exchanger as described in 8).

  10) The heat exchanger according to 9), wherein the refrigerant inlet pipe is connected to the refrigerant inlet of the joint plate, and the refrigerant outlet pipe is connected to the refrigerant outlet.

  11) The reduced diameter portion formed at the end of the refrigerant inlet pipe is inserted into the refrigerant inlet of the joint plate, and the reduced diameter portion formed at the end of the refrigerant outlet pipe is inserted into the refrigerant outlet. 10. The heat exchanger as described in 10) above, wherein the inlet pipe and the refrigerant outlet pipe are respectively joined to the joint plate.

  12) The heat exchanger according to 9) above, wherein an expansion valve mounting member having two refrigerant circulation portions communicating with the refrigerant inlet and the refrigerant outlet is joined to the joint plate.

  13) The heat exchanger according to any one of 1) to 12) above, wherein the refrigerant circulation path includes a plurality of intermediate header portions and a plurality of heat exchange tubes.

  14) A refrigerant outlet header portion is arranged on the rear side of the refrigerant inlet header portion, and a refrigerant circulation side intermediate header portion and a refrigerant outlet header portion arranged so that the refrigerant circulation path faces the refrigerant inlet header portion below the refrigerant inlet header portion. The refrigerant outflow side intermediate header portion and a plurality of heat exchange pipes arranged to face the lower portion of the refrigerant, and the refrigerant inflow side intermediate header portion and the refrigerant outflow side intermediate header portion communicate with each other. A heat exchange tube group consisting of a plurality of heat exchange tubes arranged at intervals between the inlet header portion and the refrigerant inflow side intermediate header portion and between the refrigerant outlet header portion and the refrigerant outflow side intermediate header portion. Are arranged in at least one row to form a heat exchange core part, and both ends of the heat exchange pipes constituting these heat exchange pipe groups are connected to the header parts facing each other. Heat described in any Exchanger.

  15) The refrigerant outlet header is partitioned into two spaces in the height direction by the dividing means, and a heat exchange pipe is connected so as to face the first space, and a refrigerant passage hole is formed in the dividing means. The heat exchanger according to any one of 1) to 14) above, wherein the second space of the header portion communicates with the refrigerant outlet.

  16) The heat according to any one of 1) to 15) above, wherein the refrigerant inlet header part and the refrigerant outlet header part are provided by dividing one refrigerant inlet / outlet tank forward and backward by a partitioning means. Exchanger.

  17) The refrigerant inlet / outlet tank includes a first member to which the heat exchange pipe is connected, a second member brazed to a portion of the first member opposite to the heat exchange pipe, and the first and second members. The heat exchanger according to 16) above, comprising a closing member brazed to both ends, wherein the partitioning means and the partitioning means are formed integrally with the second member.

  18) The heat exchanger according to 17) above, wherein the first member comprises an aluminum brazing sheet having a brazing material layer on at least one side.

  19) The heat exchanger according to 17) or 18) above, wherein the second member is formed of an aluminum extruded profile.

  20) The heat exchanger according to any one of 17) to 19) above, wherein the closing member comprises an aluminum brazing sheet having a brazing filler metal layer on both sides.

  21) A refrigeration cycle comprising a compressor, a condenser, and an evaporator, wherein the evaporator includes the heat exchanger according to any one of 1) to 20) above.

  22) A vehicle in which the refrigeration cycle described in 21) above is mounted as a car air conditioner.

  According to the heat exchanger of the above 1), the refrigerant inlet is formed in the closing member that closes one end opening of the refrigerant inlet header portion, and the refrigerant inlet header portion inward of the refrigerant inlet in the closing member is directed toward the inside of the refrigerant inlet header portion. Since an upwardly inclined guide is provided, the refrigerant that has flowed into the refrigerant inlet header portion through the refrigerant inlet is guided by the guide and flows obliquely upward, and the refrigerant flows in the refrigerant inlet header portion through the refrigerant inlet header portion. It becomes easy to flow to the position far from. Therefore, the refrigerant flow rates in all the heat exchange tubes connected to the refrigerant inlet header portion are made uniform, and the refrigerant flow rates in all the heat exchange tubes connected to the refrigerant outlet header portion are made uniform. As a result, the amount of refrigerant that contributes to heat exchange is made uniform with respect to the length direction of the refrigerant inlet header portion in the heat exchange core portion of the refrigerant circulation path, and the temperature of the air that has passed through the heat exchange core portion is also overall. It becomes uniform and the heat exchange performance of the heat exchanger is significantly improved. In particular, even when the flow rate of the refrigerant is small, a decrease in heat exchange performance is prevented.

  According to the heat exchanger of 2) above, since the guide is a partial spherical body, it becomes difficult for the guide to become resistance to the flow of the refrigerant.

  According to the heat exchanger of 3), the effect of the heat exchanger of 1) is remarkable.

  According to the heat exchangers 4) and 5), the effect of the heat exchanger 1) is remarkable.

  According to the heat exchanger of 6), since the closing member is common to the refrigerant inlet header part and the refrigerant outlet header part, the number of parts is reduced.

  According to the heat exchanger of the above 7), since the refrigerant inlet of the refrigerant inlet header is eccentric above the refrigerant inlet of the joint plate, the refrigerant flowing into the refrigerant inlet header through the refrigerant inlet The effect of flowing obliquely upward by the guide is further improved, and the refrigerant is more likely to flow through the refrigerant inlet header portion to a position far from the refrigerant inlet, and the effect of equalizing the refrigerant flow rate in all the heat exchange tubes is improved.

  According to the heat exchanger of the above 8), the effect by the heat exchanger of the above 7) becomes remarkable.

  According to the heat exchanger of 9) above, the joint plate is common to the refrigerant inlet header portion and the refrigerant outlet header portion, so the number of parts is reduced.

  According to the heat exchanger of 11) above, the refrigerant inlet pipe is connected to the refrigerant inlet of the joint plate and the refrigerant outlet pipe is connected to the refrigerant outlet. Since the pipe and the end of the refrigerant outlet pipe are further reduced in diameter, and the reduced diameter portion is inserted into the refrigerant inlet and the refrigerant outlet, the outer diameter of the refrigerant inlet and the refrigerant outlet can be considerably reduced. The interval between the refrigerant inlet and the refrigerant outlet can be made relatively large. Therefore, even when the dimension of the joint plate in the front-rear direction is restricted, the joint area between the refrigerant inlet and the refrigerant outlet in the joint plate and the refrigerant inlet header portion and the refrigerant outlet header portion is large. Thus, it is possible to prevent the occurrence of poor bonding, and a short circuit between the refrigerant inlet header portion and the refrigerant outlet header portion is prevented. As a result, the refrigerant flowing from the refrigerant inlet pipe is prevented from entering the refrigerant outlet pipe without passing through all the heat exchange pipes, and the cooling performance of the heat exchanger is prevented from being lowered. Further, since the reduced diameter portion is formed at the end of the refrigerant inlet pipe, the flow velocity of the refrigerant when flowing from the refrigerant inlet pipe into the refrigerant inlet header becomes high, and the refrigerant passes through the refrigerant inlet header. It becomes easy to reach the end on the opposite side, and the effect of the heat exchanger of 1) is improved.

According to the heat exchanger of the above 15), the refrigerant circulation amount of all the heat exchange pipes connected to the refrigerant inlet header is made more uniform by the function of the partition means, and connected to the refrigerant outlet header. The refrigerant circulation amount of all the heat exchange tubes is made uniform, and the heat exchange performance of the heat exchanger is further improved.
According to the heat exchanger of the above 16), the number of parts of the entire heat exchanger can be reduced.

  According to the heat exchanger of the above 17), since the partitioning means and the partitioning means of the refrigerant inlet / outlet tank are formed integrally with the second member, the work of providing the partitioning means and the partitioning means in the refrigerant inlet / outlet tank is easy. become.

  According to the heat exchanger of the above 18), the first member and the heat exchange tube are simultaneously bonded to the first member and the second member by using the brazing material layer on at least one side of the first member. Since the heat exchange pipe can be connected to the refrigerant turn-in / out tank by brazing, the manufacturing operation is simplified.

  According to the heat exchanger of the above 19), the second member of the refrigerant inlet / outlet tank can be manufactured relatively easily.

  According to the heat exchanger of 20) above, the closing member can be brazed to the first and second members using the brazing material layers on both sides of the closing member, and the joint plate is brazed to the closing member. Manufacturing process is simplified.

  Embodiments of the present invention will be described below with reference to the drawings. In this embodiment, the heat exchanger according to the present invention is applied to an evaporator for a car air conditioner.

  In the following description, the left and right in FIG.

  1 and 2 show the overall configuration of an evaporator for a car air conditioner to which the heat exchanger according to the present invention is applied, FIGS. 3 to 10 show the configuration of the main part, and FIG. 11 shows how the refrigerant flows in the evaporator.

  1 and 2, an evaporator (1) used in a car air conditioner using a chlorofluorocarbon refrigerant is composed of an aluminum refrigerant inlet / outlet tank (2) and an aluminum refrigerant turn tank arranged at intervals in the vertical direction. (3) and a heat exchange core section (4) provided between both tanks (2) and (3).

  The refrigerant inlet / outlet tank (2) includes a refrigerant inlet header portion (5) located on the front side (downstream side in the ventilation direction) and a refrigerant outlet header portion (6) located on the rear side (upstream side in the ventilation direction). . An aluminum refrigerant inlet pipe (7) is connected to the refrigerant inlet header (5) of the refrigerant inlet / outlet tank (2), and an aluminum refrigerant outlet pipe (8) is also connected to the refrigerant outlet header (6). . The refrigerant turn tank (3) includes a refrigerant inflow header portion (9) (refrigerant inflow side intermediate header portion) located on the front side and a refrigerant outflow header portion (11) (refrigerant outflow side intermediate header portion) located on the rear side. It has.

  The heat exchange core section (4) is composed of a plurality of heat exchange pipe groups (13) each including a plurality of heat exchange pipes (12) arranged in parallel at intervals in the left-right direction. Then, it is configured by arranging two rows. Corrugated fins on the outside of the heat exchange pipes (12) at the left and right ends of each heat exchange pipe group (13) and the ventilation gap between adjacent heat exchange pipes (12) of each heat exchange pipe group (13) (14) is arranged and brazed to the heat exchange pipe (12). Aluminum side plates (15) are respectively arranged outside the corrugated fins (14) at the left and right ends and brazed to the corrugated fins (14). The upper and lower ends of the heat exchange pipe (12) of the front heat exchange pipe group (13) are connected to the refrigerant inlet header part (5) and the refrigerant inflow header part (9) in a state of projecting into the rear side, respectively, The upper and lower ends of the heat exchange pipe (12) of the heat exchange pipe group (13) are connected to the refrigerant outlet header part (6) and the refrigerant outflow header part (11) in a state of projecting into the respective parts. The refrigerant inlet header (9), the refrigerant outlet header (11), and the plurality of heat exchange pipes (12) of each heat exchange pipe group (13) are used as a refrigerant inlet header (5) and a refrigerant outlet header (6). A refrigerant circulation path is formed through the

  As shown in FIGS. 3 to 6, the refrigerant inlet / outlet tank (2) is a plate-shaped first member formed of an aluminum brazing sheet having a brazing filler metal layer on both sides and connected to a heat exchange pipe (12). 16), a second member (17) made of a bare material formed from an aluminum extruded shape and covering the upper side of the first member (16), and an aluminum brazing sheet having a brazing filler metal layer on both sides. It consists of aluminum caps (18), (19) (closing members) that are joined to both ends of the members (16), (17) to close the left and right end openings, and on the outer surface of the right cap (19), An aluminum joint plate (21) which is long in the front-rear direction is brazed so as to straddle 5) and the refrigerant outlet header portion (6). A refrigerant inlet pipe (7) and a refrigerant outlet pipe (8) are connected to the joint plate (21).

  The first member (16) has curved portions (22) having a small cross-sectional arc shape with a central portion projecting downward at both front and rear side portions thereof. A plurality of tube insertion holes (23) that are long in the front-rear direction are formed in each bending portion (22) at intervals in the left-right direction. The tube insertion holes (23) of the front and rear curved portions (22) are at the same position in the left-right direction. Standing walls (22a) are integrally formed over the entire length at the front edge of the front curved portion (22) and the rear edge of the rear curved portion (22), respectively. In addition, a plurality of through holes (25) are formed at intervals in the left-right direction in the flat portion (24) between the curved portions (22) of the first member (16).

  The second member (17) has a substantially m-shaped cross section that opens downward, and is provided in the center between the front and rear walls (26) extending in the left-right direction and the front and rear walls (26) and extends in the left-right direction. A partition wall (27) as a partition means for partitioning the refrigerant inlet / outlet tank (2) into two front and rear spaces, and upper ends of the front and rear walls (26) and the partition wall (27) are integrally connected to each other. Two projecting substantially arc-shaped connecting walls (28) are provided. The lower end portion of the rear wall (26) of the second member (17) and the lower end portion of the partition wall (27) are compartments that divide the refrigerant outlet header portion (6) into two upper and lower spaces (6a) and (6b). It is integrally connected over the entire length by a shunt resistor plate (29) as means. A plurality of refrigerant passage holes (31A) (31B) that are long in the left-right direction are formed in a penetrating manner at intervals in the left-right direction in the portion excluding the left and right end portions in the rear portion of the shunt resistor plate (29). ing. The lower end of the partition wall (27) protrudes downward from the lower ends of the front and rear walls (26), and a plurality of lower walls protrude downward and are fitted into the through holes (25) of the first member (16). The protrusions (27a) are integrally formed with an interval in the left-right direction. The protrusion (27a) is formed by cutting a predetermined portion of the partition wall (27).

  As shown in FIGS. 7 to 9, the right cap (19) has a first closing part (19A) for closing the right end opening of the refrigerant inlet header part (5) and a right end opening of the refrigerant outlet header part (6). And a second closing portion (19B) for closing. The first closing part (19A) of the right cap (19) is integrally formed with a left protruding part (32) fitted into the refrigerant inlet header part (5), and is also formed on the second closing part (19B). The upper left projecting portion (33) fitted into the space (6a) above the shunt resistor plate (29) of the refrigerant outlet header (6) and the shunt resistor plate (29). A lower left projecting portion (34) fitted into the side space (6b) is integrally formed with a space in the vertical direction. A circular refrigerant inlet (37) is formed in the bottom wall (32a) of the front left protrusion (32) in the right cap (19), and the refrigerant is also applied to the entire bottom wall of the rear upper left protrusion (33). An outlet (38) is formed. The inner diameter of the refrigerant inlet (37) is preferably 3 to 8.5 mm. The inner surface of the bottom wall (32a) of the left protrusion (32) of the right cap (19) is vertical, and the refrigerant inlet header is formed on the lower arc edge of the refrigerant inlet (37) on the inner surface of the bottom wall (32a). A guide (40) inclined upward toward the inside (left) of the portion (5) is integrally formed. The guide (40) is a partial spherical body constituting a part of the spherical body, and the protruding end surface (40a) of the guide (40) is inclined with respect to the bottom wall (32a) of the left protruding portion (32). Located on the slope (F). An inferior angle α formed by the inclined surface (F) where the protruding end surface (40a) of the guide (40) is located and the inner surface of the bottom wall (32a) of the left protruding portion (32) is 15 to 60 degrees. It is preferable (see FIG. 9). In addition, an engaging claw (35) protruding leftward is formed integrally with the arc-shaped portion between the front and rear side edges and the upper edge of the right cap (19). Further, an engaging claw (36) projecting leftward is formed integrally with the front side portion and the rear side portion of the lower edge of the right cap (19).

  The left cap (18) is symmetrical with the right cap (19), and the rightward projecting portion (39) fitted into the refrigerant inlet header portion (5) and the shunt resistor plate of the refrigerant outlet header portion (6) Upper right protrusion (41) that fits in space (6a) above (29), lower right that fits in space (6b) below shunt resistor plate (29) The projecting portion (42) and the upper and lower engaging claws (43) and (44) projecting to the right are integrally formed. No opening is formed in the bottom wall of the right protrusion (39) and the upper right protrusion (41). The upper edges of the caps (18) and (19) have two substantially arcuate portions at the center in the front-rear direction so that they coincide with both ends of the upper surface of the second member (17) of the refrigerant inlet / outlet tank (2). It is shaped like a single piece. In addition, the lower edges of the caps (18) and (19) have two substantially arcuate portions in the center in the front-rear direction so as to match both ends of the lower surface of the first member (16) of the refrigerant inlet / outlet tank (2). In FIG. 1, the shape is such that they are connected together through a flat portion.

  The joint plate (21) has a short cylindrical refrigerant inlet (45) leading to the refrigerant inlet (37) of the right cap (19) and a short cylindrical refrigerant outlet (46) also leading to the refrigerant outlet (38). I have. The refrigerant inlet (45) and the refrigerant outlet (46) are respectively a circular through hole (45a) (46a) and a short cylinder integrally formed to protrude rightward around the through holes (45a) (46a). It consists of a shape part (45b) (46b). The centers of the refrigerant inlet (45) and the refrigerant outlet (46) are at the same height. The outer diameter of the short cylindrical portion (45b) of the refrigerant inlet (45) is smaller than the outer diameter of the short cylindrical portion (46b) of the refrigerant outlet (46). The refrigerant inlet (37) of the right cap (19) is eccentric above the circular through hole (45a) of the refrigerant inlet (45). The eccentric amount P is preferably 0.5 to 3 mm (see FIG. 9). The length in the front-rear direction of the joint plate (21) is preferably 50 mm or less, and the distance between the refrigerant inlet (45) and the refrigerant outlet (46) is preferably 6 to 9 mm.

  In the joint plate (21) between the refrigerant inlet (45) and the refrigerant outlet (46), slits (47) for preventing a short circuit extending in the vertical direction are formed, and both upper and lower ends of the slit (47). A substantially triangular through hole (48) (49) is formed in a row. The width in the front-rear direction of the slit (47) is preferably 1 mm or less. Further, the upper part of the upper through hole (48) and the lower part of the lower through hole (49) of the joint plate (21) are bent so as to protrude to the left, and bent parts (51) (54) are formed. Is formed. The upper bent portion (51) is an engagement portion formed between the refrigerant inlet header portion (5) and the refrigerant outlet header portion (6), that is, two substantially arcuate shapes at the upper edge of the right cap (19). Engaging part (52) formed between the two parts, and engaging part (53) formed between the two connecting walls (28) of the second member (17) of the refrigerant inlet / outlet tank (2). Match. The lower bent portion (54) is an engagement portion formed between the refrigerant inlet header portion (5) and the refrigerant outlet header portion (6), that is, two substantially circles at the lower edge of the right cap (19). The engaging portion (55) formed between the arc-shaped portions and formed by the flat portion, and the engaging portion (56) formed by the flat portion (24) of the first member (16) of the refrigerant inlet / outlet tank (2). Is engaged. Further, engaging claws (57) protruding leftward are integrally formed at both front and rear ends of the lower edge of the joint plate (21). The engaging claw (57) is engaged with the right cap (19) in a state of being fitted in a recess (19a) formed at the lower edge of the right cap (19).

  The reduced diameter portion (7a) formed at one end of the refrigerant inlet pipe (7) is inserted into the refrigerant inlet (45) of the joint plate (21) and brazed, and the refrigerant outlet (46) (46 ), A reduced diameter portion (8a) formed at one end of the refrigerant outlet pipe (8) is inserted and brazed. Although not shown, an expansion valve mounting member is joined to the other ends of the refrigerant inlet pipe (7) and the refrigerant outlet pipe (8) so as to straddle both pipes (7) and (8).

  The first and second members (16), (17), the caps (18), (19), and the joint plate (21) of the refrigerant inlet / outlet tank (2) are brazed as follows. That is, the first and second members (16), (17) are inserted into the through holes (25) of the first member (16) by the protrusions (27a) of the second member (17) and caulked. The brazing material of the first member (16) in a state where the upper ends of the rising walls (22a) before and after the one member (16) and the lower ends of both front and rear walls (26) of the second member (17) are engaged. They are brazed together using layers. Both caps (18) and (19) are arranged so that the front protrusions (39) and (32) are in the space on the front side of the partition walls (27) in both members (16) and (17), and the rear upper protrusions ( 41) (33) is located behind the partition wall (27) in both members (16) and (17) and above the shunt resistor plate (29), and the rear lower protrusion (42 ) (34) are respectively fitted in the spaces behind the partition wall (27) and below the shunt resistor plate (29), and the upper engaging claws (43) (35) are second With the lower engaging claws (44) (36) engaged with the curved portion (22) of the first member (16) engaged with the connecting wall (28) of the member (17), The first and second members 16 and 17 are brazed using the brazing material layers of both caps 18 and 19. In the joint plate (21), the upper bent portion (51) is engaged with the upper engaging portion (52) of the right cap (19) and the engaging portion (53) of the second member (17). The bent portion (54) is engaged with the lower engaging portion (55) of the right cap (19) and the engaging portion (56) of the first member (16), and the engaging claw (57) is on the right side. The right side cap (19) using the brazing filler metal layer of the right side cap (19) in a state of fitting in the recess (19a) formed on the lower edge of the cap (19) and engaging the right side cap (19). It is brazed.

  Thus, the refrigerant inlet / outlet tank (2) is formed, the refrigerant inlet header portion (5) on the front side of the partition wall (27) of the second member (17) and the refrigerant on the rear side of the partition wall (27). It is the exit header (6). The refrigerant outlet header (6) is divided into upper and lower spaces (6a) and (6b) by a shunt resistor plate (29), and these spaces (6a) and (6b) are formed in the refrigerant passage holes (31A) ( 31B). The refrigerant outlet (38) of the right cap (19) communicates with the upper space (6a) of the refrigerant outlet header (6). Further, the refrigerant inlet (45) of the joint plate (21) is communicated with the refrigerant inlet (37), and the refrigerant outlet (46) is communicated with the refrigerant outlet (38).

  As shown in FIGS. 4 and 10, the refrigerant turn tank (3) is formed of an aluminum brazing sheet having a brazing filler metal layer on both sides and is connected to a plate-shaped first member (12) connected to a heat exchange pipe (12). 70), a second member (71) made of a bare material formed from an aluminum extruded profile and covering the lower side of the first member (70), and an aluminum brazing sheet having a brazing filler metal layer on both sides; It consists of an aluminum cap (72) that closes the left and right opening.

  The top surface (3a) of the refrigerant turn tank (3) has a central part in the front-rear direction as the highest part (73) and gradually decreases from the highest part (73) toward the front and rear sides. The cross section is formed in a circular arc shape. Grooves (74) extending from the front and rear sides of the highest portion (73) on the top surface (3a) to the front and rear sides (3b) are spaced at the left and right sides of the refrigerant turn tank (3). A plurality are formed.

  The first member (70) has a cross-sectional arc shape in which a central portion in the front-rear direction protrudes upward, and a hanging wall (70a) is integrally formed over the entire length on both front and rear edges. The upper surface of the first member (70) is the top surface (3a) of the refrigerant turn tank (3), and the outer surface of the hanging wall (70a) is the front and rear side surfaces (3b) of the refrigerant turn tank (3). ing. On both the front and rear sides of the first member (70), a groove (74) is formed from the highest position (73) at the center in the front-rear direction to the lower end of the hanging wall (70a). A long tube insertion hole (75) is formed in the front-rear direction between adjacent grooves (74) in the front and rear side portions excluding the highest portion (73) of the first member (70). The front and rear pipe insertion holes (75) are at the same position in the left-right direction. A plurality of through holes (76) are formed at intervals in the left-right direction in the highest position (73) of the first member (70). The first member (70) is formed by simultaneously forming the hanging wall (70a), the groove (74), the tube insertion hole (75), and the through hole (76) by pressing the aluminum brazing sheet. .

  The second member (71) has a substantially w-shaped cross section opened upward, and extends between the front and rear walls (77) and the front and rear walls (77) extending in the left-right direction curved upward toward the outer side in the front-rear direction. A vertical partition wall (78) as a partition means provided in the center and extending in the left-right direction and partitioning the refrigerant turn tank (3) into two front and rear spaces, both front and rear walls (77) and partition walls (78 ) And two connecting walls (79) for connecting the lower ends of the two together. The upper end of the partition wall (78) protrudes upward from the upper ends of the front and rear walls (77), and a plurality of upper walls protrude upward and are fitted into the through holes (76) of the first member (70). The protrusions (78a) are integrally formed at intervals in the left-right direction. Further, a coolant passage notch (78b) is formed between adjacent protrusions (78a) on the partition wall (78) from the upper edge thereof. The protrusion (78a) and the notch (78b) are formed by cutting a predetermined portion of the partition wall (78).

  The second member (71) is formed by integrally extruding both the front and rear walls (77), the partition wall (78), and the connecting wall (79), and then cutting the partition wall (78) to form protrusions (78a) and notches Manufactured by forming (78b).

  On the front side of each cap (72), a leftward and rightward projecting portion (81) that is fitted into the refrigerant inflow header portion (9) is integrally formed, and on the rear side, the refrigerant outflow header portion ( 11) A projecting portion (82) inward in the left-right direction that is fitted into the inside is integrally formed. In addition, an engaging claw (83) projecting inward in the left-right direction is integrally formed on the arc-shaped portion between the front and rear side edges and the lower edge of each cap (72), and is also formed in the left-right direction at the upper edge. A plurality of engaging claws (84) projecting in the direction are integrally formed at intervals in the front-rear direction.

  The first and second members (70) and (71) of the refrigerant turn tank (3) and the caps (72) are brazed as follows. The first and second members (70) and (71) are drooped before and after the first member (70) when the projection (78a) of the second member (71) is inserted into the through hole (76) and caulked. With the lower end of the wall (70a) and the upper end of both front and rear walls (77) of the second member (71) engaged, the brazing material layer of the first member (70) is used to braze each other. It is attached. Both caps (72) have front protrusions (81) in the space in front of the partition walls (78) of both members (70) (71), and rear protrusions (82) have both members (70 ) (71) are respectively fitted into the spaces behind the partition wall (78), and the upper engaging claw (84) is engaged with the first member (70), so that the lower engaging claw is engaged. With the (83) engaged with the front and rear walls (77) of the second member (71), the first and second members (70), (71) are utilized using the brazing material layer of each cap (72). ) Is brazed. Thus, the refrigerant turn tank (3) is formed, the refrigerant inflow header portion (9) on the front side of the partition wall (78) of the second member (71) and the refrigerant on the rear side of the partition wall (78). It is an outflow header (11). The upper end opening of the notch (78b) of the partition wall (78) of the second member (71) is closed by the first member (70), thereby forming a refrigerant passage hole (85). The refrigerant inflow header portion (9) and the refrigerant outflow header portion (11) are communicated with each other through the refrigerant passage hole (85).

  The heat exchange pipe (12) constituting the front and rear heat exchange pipe group (13) is made of an aluminum extruded profile, and has a wide flat shape in the front and rear direction, and a plurality of refrigerant passages (12a) extending in the length direction therein. Are formed in parallel (see FIG. 6). The upper end of the heat exchange pipe (12) is inserted into the pipe insertion hole (23) of the first member (16) of the refrigerant inlet / outlet tank (2), and the brazing material layer of the first member (16) is used. The first member (16) is brazed to the first member (70), and the lower end of the first member (70) is inserted into the pipe insertion hole (75) of the first member (70) of the refrigerant turn tank (3). ) Is brazed to the first member (70) using the brazing material layer.

  Here, the tube height which is the thickness in the left-right direction of the heat exchange tube (12) is 0.75 to 1.5 mm, the tube width which is the width in the front-rear direction is 12 to 18 mm, and the wall thickness of the peripheral wall is 0.175 to 0.275 mm, the thickness of the partition wall partitioning the refrigerant passages is 0.175 to 0.275 mm, the pitch of the partition walls is 0.5 to 3.0 mm, and the curvature radius of the outer surfaces of the front and rear end walls is 0.35 to 0 .75 mm is preferable.

  As the heat exchange pipe (12), instead of one made of an aluminum extruded shape, a pipe in which a plurality of refrigerant passages are formed by inserting inner fins into an aluminum electric sewing pipe may be used. . Also, two flat wall forming portions formed by rolling on the brazing filler metal layer side of an aluminum brazing sheet having a brazing filler metal layer on one side and connected via a connecting portion, and connection in each flat wall forming portion A side wall forming portion integrally formed in a raised shape from the side edge opposite to the portion, and a plurality of integrally formed in a raised shape from both flat wall forming portions at a predetermined interval in the width direction of the flat wall forming portion. A plate provided with a partition wall forming portion may be bent into a hairpin shape at the connecting portion, the side wall forming portions are brought into contact with each other and brazed to each other, and a partition wall is formed by the partition wall forming portion.

  The corrugated fin (14) is formed in a wave shape using an aluminum brazing sheet having a brazing filler metal layer on both sides, and a plurality of the corrugated fins (14) are connected in parallel in the front-rear direction to the connecting portion connecting the wave head and the wave bottom. A louver is formed. The corrugated fin (14) is shared by both the front and rear heat exchange tube group (13), and the width in the front and rear direction is the heat exchange tube (12) front edge of the front heat exchange tube group (13) and the rear heat exchange. The distance between the rear edge of the heat exchanger tube (12) of the tube group (13) is substantially equal. Here, the linear distance between the wave head and the wave bottom, which is the fin height of the corrugated fin (14), is 7.0 mm to 10.0 mm, and the pitch of the connecting portion which is also the fin pitch is 1.3 to 1.8 mm. It is preferable that In addition, instead of sharing one corrugated fin between the front and rear heat exchange tube groups (13), corrugated fins are respectively arranged between adjacent heat exchange tubes (12) of both heat exchange tube groups (13). It may be.

  The evaporator (1) is manufactured by temporarily fixing a combination of the constituent members excluding the refrigerant inlet pipe (7) and the refrigerant outlet pipe (8), and brazing all the constituent members together.

  The evaporator (1) constitutes a refrigeration cycle together with a compressor and a condenser, and is mounted on a vehicle such as an automobile as a car air conditioner.

  In the above-described evaporator (1), as shown in FIG. 11, the gas-liquid mixed phase two-layer refrigerant that has passed through the compressor, the condenser, and the expansion valve flows from the refrigerant inlet pipe (7) to the refrigerant inlet of the joint plate (21). (45) and the refrigerant inlet (37) of the right side cap (19) through the refrigerant inlet / outlet section (5) of the refrigerant inlet / outlet tank (2) to be divided into all the front heat exchange pipe groups (13). Into the refrigerant passage (12a) of the heat exchange pipe (12).

  At this time, since the refrigerant inlet (37) is eccentric above the refrigerant inlet (45), the refrigerant flows obliquely upward to the left from the refrigerant inlet (45) toward the refrigerant inlet (37). (40) is guided to flow obliquely upward to the left, and the refrigerant becomes easy to flow to the left end portion in the refrigerant inlet header (5), and all the heat exchange tubes (13) of the front heat exchange tube group (13) ( 12) Evenly flows into. Further, when the inner diameter of the reduced diameter portion (7a) of the refrigerant inlet pipe (7) is 3 to 8.5 mm, the flow rate of the refrigerant sent from the refrigerant inlet pipe (7) becomes high, so that the refrigerant is It becomes easy to flow in the refrigerant inlet header part (5) to the left end part, and flows uniformly into all the heat exchange pipes (12) of the front heat exchange pipe group (13). Therefore, the refrigerant flow rates in all the heat exchange tubes (12) of the front heat exchange tube group (13) connected to the refrigerant inlet header (5) are made uniform.

  The refrigerant that has flowed into the refrigerant passages (12a) of all the heat exchange tubes (12) flows downward in the refrigerant passages (12a) and enters the refrigerant inflow header portion (9) of the refrigerant turn tank (3). . The refrigerant that has entered the refrigerant inflow header portion (9) enters the refrigerant outflow header portion (11) through the refrigerant passage hole (85) of the partition wall (78).

  The refrigerant that has entered the refrigerant outflow header section (11) is divided and flows into the refrigerant passages (12a) of all the heat exchange pipes (12) in the rear heat exchange pipe group (13), changing the flow direction. Then, it flows upward in the refrigerant passage (12a) and enters the lower space (6b) of the refrigerant outlet header (6). Here, the refrigerant flow rate in the heat exchange pipes (12) of the front heat exchange pipe group (13) connected to the refrigerant inlet header part (5) is made uniform, so that the refrigerant outlet header part ( The refrigerant flow rates in all the heat exchange tubes (12) of the rear heat exchange tube group (13) connected to 6) are also equalized. Further, since resistance is imparted to the refrigerant flow by the shunt resistor plate (29), the shunt flow from the refrigerant outflow header (11) to all the heat exchange pipes (12) in the rear heat exchange pipe group (13) Is made uniform, and the branch flow from the refrigerant inlet header portion (5) to all the heat exchange tubes (12) of the front heat exchange tube group (13) is further uniformized. As a result, the refrigerant flow rate of all the heat exchange tubes (12) in both heat exchange tube groups (13) is made uniform.

  Next, the refrigerant enters the upper space (6a) of the refrigerant outlet header (6) through the refrigerant passage holes (31A) and (31B) of the shunt resistor plate (29), and enters the refrigerant outlet of the right cap (19) ( 38) and the refrigerant outlet (46) of the joint plate (21), and flows out to the refrigerant outlet pipe (8). The refrigerant passes through the refrigerant passage (12a) of the heat exchange tube (12) of the front heat exchange tube group (13) and the refrigerant passage (12a) of the heat exchange tube (12) of the rear heat exchange tube group (13). During the flow, the ventilation gap exchanges heat with the air flowing in the direction indicated by the arrow X in FIG.

  Here, the refrigerant flow rate in all the heat exchange pipes (12) of the front heat exchange pipe group (13) connected to the refrigerant inlet header part (5) is made uniform, and the refrigerant outlet header part (6) As a result of the uniform flow rate of the refrigerant in all the heat exchange tubes (12) of the rear heat exchange tube group (13) connected to the heat exchange core portion (4) The temperature of the air that has passed through the heat exchange core section (4) is made uniform as a whole, and the heat exchange performance of the evaporator (1) is remarkably improved. In particular, even when the flow rate of the refrigerant is small, a decrease in heat exchange performance is prevented.

  Further, the refrigerant passes through the refrigerant passage (12a) of the heat exchange pipe (12) of the front heat exchange pipe group (13) and the refrigerant passage (12a) of the heat exchange pipe (12) of the rear heat exchange pipe group (13). When the heat exchange with the air flowing through the ventilation gap in the direction indicated by the arrow X in FIG. 1 occurs during the flow, condensed water is generated on the surface of the corrugated fin (14), and this condensed water is stored in the refrigerant turn tank (3 ) Flows down to the top surface (3a). The condensed water flowing down to the top surface (3a) of the refrigerant turn tank (3) enters the groove (74) by the capillary effect, flows in the groove (74), and flows from the outer end in the front-rear direction to the refrigerant turn tank. Drop down (3). In this way, freezing of condensed water caused by accumulation of a large amount of condensed water between the top surface (3a) of the refrigerant turn tank (3) and the lower end of the corrugated fin (14) is prevented, and as a result, the evaporator (1 ) Performance degradation is prevented.

  In the above embodiment, between the refrigerant inlet header portion (5) and the refrigerant inflow header portion (9) of both tanks (2) and (3), and the refrigerant outlet header portion (6) and the refrigerant outflow header portion (11). However, the present invention is not limited to this, and the refrigerant inlet header portion (5) and the refrigerant inflow header portion of both tanks (2) and (3) are not limited to this. One or two or more heat exchange pipe groups (13) may be provided between the refrigerant outlet header section (6) and the refrigerant outlet header section (11).

  In the above embodiment, the refrigerant inlet pipe (7) is connected to the refrigerant inlet (45) of the joint plate (21), the refrigerant outlet pipe (8) is connected to the refrigerant outlet (46), and the refrigerant inlet pipe (7 ) And the refrigerant outlet pipe (8), and the expansion valve mounting member is fixed across the tip of the refrigerant outlet pipe (8). Alternatively, the expansion valve mounting member may be joined directly to the joint plate (21).

  Furthermore, in the said embodiment, although the heat exchanger by this invention is applied to the evaporator, it is not limited to this, It can apply also to other various heat exchangers.

1 is a partially cutaway perspective view showing an overall configuration of an evaporator to which a heat exchanger according to the present invention is applied. It is the vertical sectional view which omitted the intermediate part of the evaporator shown in FIG. It is a disassembled perspective view of the part of the refrigerant | coolant in / out tank. It is the AA line expanded sectional view of Drawing 2 which omitted some. It is the BB expanded sectional view of FIG. 2 which abbreviate | omitted one part. It is CC sectional view taken on the line of FIG. It is a disassembled perspective view which expands and shows the tank for a refrigerant | coolant in / out, a right side cap, and a joint plate. It is a perspective view of a right side cap. FIG. 3 is a partially enlarged view of FIG. 2. It is a disassembled perspective view of the part of the tank for refrigerant | coolant turns. It is a figure which shows how the refrigerant | coolant flows in the evaporator shown in FIG.

Explanation of symbols

(1): Evaporator (heat exchanger)
(2): Refrigerant tank
(3): Refrigerant turn tank
(4): Heat exchange core
(5): Refrigerant inlet header
(6): Refrigerant outlet header
(7): Refrigerant inlet pipe
(7a): Reduced diameter part
(8): Refrigerant outlet pipe
(8a): Reduced diameter part
(9): Refrigerant inflow header
(11): Refrigerant outflow header
(12): Heat exchange pipe
(13): Heat exchange tube group
(16): First member
(17): Second member
(19): Cap (closing member)
(19A): First closure
(19B): Second closure
(21): Joint plate
(27): Partition wall (partitioning means)
(29): Resistive plate for shunting (compartment means)
(32): Left protrusion
(32a): Bottom wall
(37): Refrigerant inlet
(38): Refrigerant outlet
(40): Guide
(40a): Projected end face
(45): Refrigerant inlet
(46): Refrigerant outlet
(F): Inclined surface P: Eccentricity α: Angle

Claims (22)

A refrigerant inlet header portion and a refrigerant outlet header portion arranged side by side in the front-rear direction at the upper end portion, and a refrigerant circulation path passing through both header portions, and a refrigerant inlet is formed at one end of the refrigerant inlet header portion The refrigerant outlet is formed at the same end as the refrigerant inlet in the refrigerant outlet header, and the refrigerant flowing into the refrigerant inlet header from the refrigerant inlet returns to the refrigerant outlet header through the refrigerant circulation path and is sent out from the refrigerant outlet. In the heat exchanger
The refrigerant inlet is formed in a closing member that closes one end opening of the refrigerant inlet header portion, and a guide that is inclined upward toward the inside of the refrigerant inlet header portion is provided at a lower edge of the refrigerant inlet in the closing member. Exchanger. The heat exchanger according to claim 1, wherein the guide is a partial spherical body. The heat exchanger according to claim 1 or 2, wherein the refrigerant inlet of the refrigerant inlet header is circular, and the inner diameter thereof is 3 to 8.5 mm. The heat exchanger according to any one of claims 1 to 3, wherein the protruding end surface of the guide is located on an inclined surface inclined with respect to a vertical inner surface of the closing member. The heat exchanger according to claim 4, wherein an inferior inclination angle formed by the inclined surface on which the protruding end surface of the guide is located and the vertical inner surface of the closing member is 15 to 60 degrees. The closing member has a first closing portion that closes one end opening of the refrigerant inlet header portion, and a second closing portion that closes an opening at the same end as the refrigerant inlet in the refrigerant outlet header portion, and the first closing portion The heat exchanger according to any one of claims 1 to 5, wherein a refrigerant inlet is formed in the first guide, a guide is provided, and a refrigerant outlet is formed in the second closing portion. A joint plate having a refrigerant inlet leading to the refrigerant inlet of the closing member is joined to one end of the refrigerant inlet header, and the refrigerant inlet of the refrigerant inlet header is eccentric above the refrigerant inlet of the joint plate. Item 7. The heat exchanger according to any one of Items 1 to 6. The heat exchanger according to claim 7, wherein an eccentric amount of the refrigerant inlet of the refrigerant inlet header portion with respect to the refrigerant inlet of the joint plate is 0.5 to 3 mm. The joint plate is joined across the refrigerant inlet header portion and the refrigerant outlet header portion, and a refrigerant outlet port leading to the refrigerant outlet is formed in the joint plate in addition to the refrigerant inlet port leading to the refrigerant inlet. The described heat exchanger. The heat exchanger according to claim 9, wherein a refrigerant inlet pipe is connected to the refrigerant inlet of the joint plate, and a refrigerant outlet pipe is connected to the refrigerant outlet. A reduced diameter portion formed at the end of the refrigerant inlet pipe is inserted into the refrigerant inlet of the joint plate, and a reduced diameter portion formed at the end of the refrigerant outlet pipe is inserted into the refrigerant outlet, and the refrigerant inlet pipe The heat exchanger according to claim 10, wherein the refrigerant outlet pipe and the refrigerant outlet pipe are respectively joined to the joint plate. The heat exchanger according to claim 9, wherein an expansion valve mounting member having two refrigerant circulation portions communicating with the refrigerant inlet and the refrigerant outlet is joined to the joint plate. The heat exchanger according to any one of claims 1 to 12, wherein the refrigerant circulation path includes a plurality of intermediate header portions and a plurality of heat exchange tubes. A refrigerant outlet header portion is disposed behind the refrigerant inlet header portion, and a refrigerant circulation path is disposed below the refrigerant inlet header portion so as to face the refrigerant inlet header portion, below the refrigerant inlet header portion and the refrigerant outlet header portion. The refrigerant outflow side intermediate header portion and the plurality of heat exchange pipes are arranged so as to face each other, and the refrigerant inflow side intermediate header portion and the refrigerant outflow side intermediate header portion are communicated with each other, and the refrigerant inlet header At least a heat exchange tube group composed of a plurality of heat exchange tubes arranged with a space between the first portion and the refrigerant inflow side intermediate header portion, and between the refrigerant outlet header portion and the refrigerant outflow side intermediate header portion. The heat exchange core part is formed by being arranged in a row, and both end parts of the heat exchange pipes constituting these heat exchange pipe groups are connected to header parts facing each other. Described Exchanger. The refrigerant outlet header is partitioned into two spaces in the height direction by the partitioning means, and a heat exchange pipe is connected so as to face the first space, a refrigerant passage hole is formed in the partitioning means, and the refrigerant outlet header part The heat exchanger according to claim 1, wherein the second space communicates with the refrigerant outlet. The heat exchanger according to any one of claims 1 to 15, wherein the refrigerant inlet header portion and the refrigerant outlet header portion are provided by dividing the inside of one refrigerant inlet / outlet tank forward and backward by partition means. The refrigerant inlet / outlet tank includes a first member connected to the heat exchange pipe, a second member brazed to a portion of the first member opposite to the heat exchange pipe, and both ends of the first and second members. The heat exchanger according to claim 16, comprising a brazed closure member, wherein the partition means and the partition means are formed integrally with the second member. The heat exchanger according to claim 17, wherein the first member is made of an aluminum brazing sheet having a brazing filler metal layer on at least one side. The heat exchanger according to claim 17 or 18, wherein the second member is made of an aluminum extruded profile. The heat exchanger according to any one of claims 17 to 19, wherein the closing member is made of an aluminum brazing sheet having a brazing filler metal layer on both sides. A refrigeration cycle comprising a heat exchanger according to any one of claims 1 to 20, comprising a compressor, a condenser, and an evaporator. A vehicle in which the refrigeration cycle according to claim 21 is mounted as a car air conditioner.

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