JP2007322007A - Heat exchange pipe and evaporator - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an evaporator capable of reducing difference in temperatures of the air supplied into a cabin between ON and OFF of a compressor. <P>SOLUTION: This evaporator comprises a plurality of flat heat exchange pipes 34 disposed at horizontal intervals while determining the width direction in the longitudinal direction, and extending in the vertical direction. The heat exchange pipes 34 have plurality of refrigerant passages 34a arranged in the width direction. The relationship of 0.558≤A≤1.235 is satisfied when a value obtained by dividing the number of refrigerant passages 34a of the heat exchange pipes 34 by the width W in the longitudinal direction of the heat exchange pipe 34 is A. Further the relationship of 0.35≤Dh≤1.0 is satisfied when an equivalent diameter of the heat exchange pipe 34 is Dh. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

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

  In this specification and claims, the downstream side (direction indicated by arrow X in FIG. 1) of the air flowing through the ventilation gap between adjacent heat exchange tubes is referred to as the front, and the opposite side is referred to as the rear. The top and bottom and the left and right in FIG. In this specification, the term “aluminum” includes aluminum alloys in addition to pure aluminum.

  Conventionally, as a car air conditioner evaporator, 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 corrugated fins are arranged between adjacent flat hollow bodies So-called laminated evaporators brazed to a flat hollow body have been widely used.

  Incidentally, in recent years, there has been a demand for further reduction in size and weight and higher performance of the evaporator. In addition, high performance here is the cooling performance at the time of ON of the compressor used for a car air conditioner. And as an evaporator satisfying such a requirement, a heat exchange core section constituted by arranging two rows of heat exchange pipes arranged in the front-rear direction, each of which is composed of a plurality of heat exchange pipes arranged at intervals, A refrigerant inlet header portion arranged on the upper end side of the heat exchange pipe and connected to the left half heat exchange pipe of the front heat exchange pipe group, and on the rear side of the refrigerant inlet header section on the upper end side of the heat exchange pipe A refrigerant outlet header portion arranged and connected to the heat exchange pipe in the left half of the rear heat exchange pipe group, and a heat exchange arranged on the lower end side of the heat exchange pipe and connected to the refrigerant inlet header portion A first intermediate header portion to which the heat exchange pipe of the tube group is connected, and a second intermediate header portion that is arranged on the right side of the first intermediate header portion and to which the remaining heat exchange tubes of the front heat exchange pipe group are connected. The upper end side of the heat exchange pipe is disposed on the right side of the refrigerant inlet header. And the 3rd middle header part to which the heat exchange pipe connected to the 2nd middle header part was connected, and the rear side heat exchange pipe arranged at the back of the 3rd middle header part in the upper end side of a heat exchange pipe A fourth intermediate header portion to which the remaining heat exchange pipes of the group are connected, and a heat exchange disposed on the rear side of the second intermediate header section on the lower end side of the heat exchange pipe and connected to the fourth intermediate header section A fifth intermediate header portion to which the pipe is connected, and a sixth intermediate portion to which the heat exchange pipe connected to the refrigerant outlet header portion is disposed on the left side of the fifth intermediate header portion on the lower end side of the heat exchange pipe A header portion, and the refrigerant flowing into the refrigerant inlet header portion flows into the refrigerant outlet header portion through the first to sixth intermediate header portions through the heat exchange pipe, and flows out from the refrigerant outlet header portion. Evaporators made to have been proposed (and Bas see Patent Document 1). The heat exchange tube used in the evaporator described in Patent Document 1 is formed in a flat shape in which the width direction faces the ventilation direction by bending an aluminum plate, and the inner fin is arranged in the width to thereby reduce the width. A plurality of passages arranged in the direction are formed.

  In general, when a fixed displacement compressor is used as a compressor for a car air conditioner equipped with an evaporator, the thermistor detects the air temperature (air discharge temperature) on the outlet side of the evaporator, and the compressor is periodically operated based on the detected air discharge temperature. It is controlled to repeatedly turn on and off. That is, as shown by a broken line in FIG. 12, when the discharged air temperature falls to a preset low temperature side set temperature (t1) when the compressor is turned on, the compressor is turned off, and then the discharged air temperature rises and the preset high temperature is set. The compressor is controlled to turn on when the side set temperature (t2) is reached. Therefore, when the compressor is on and when it is off, relatively cold air and relatively hot air are blown into the interior of the automobile at a constant cycle.

In recent years, it has been considered to reduce the temperature difference between the air blown into the passenger compartment when the compressor is on and off for the purpose of further improving the comfort in the passenger compartment of the automobile. By the way, in the evaporator described in Patent Document 1, in order to reduce the temperature difference between the air blown into the passenger compartment when the compressor is on and off, the high temperature side set temperature (t2) is lowered to lower the low temperature side set temperature ( It is an easy way to reduce the temperature difference between t1) and the high temperature side set temperature (t2), but in this case, the compressor will frequently turn on and off, which may adversely affect the fuel efficiency of the car. There is.
JP 2003-214794 A

  An object of the present invention is to provide a heat exchange pipe and an evaporator that can solve the above-described problems and can reduce the temperature difference of the air blown into the vehicle compartment when the compressor is on and off when used in an evaporator. It is to provide.

  As a result of various studies, the present inventors have focused on the heat exchange pipe and improved the liquid retention performance in the passage of the heat exchange pipe used in the evaporator, thereby turning on the compressor for the air blown into the vehicle interior. It was found that the temperature difference between the hour and the off time can be reduced. That is, heat exchange between the remaining liquid-phase refrigerant and the air passing through the evaporator continues while the liquid-phase refrigerant remains in the passage of the heat exchange pipe of the evaporator even after the compressor is turned off. As a result, it has been found that it is possible to suppress a rapid rise in the discharge temperature.

  The present invention has been completed based on such knowledge and comprises the following aspects.

1) A heat exchange pipe that is flat and has a plurality of passages arranged in the width direction,
A heat exchange tube that satisfies the relationship of 0.558 ≦ A ≦ 1.235, where A (pieces / mm) is the value obtained by dividing the number of passages by the width in the front-rear direction.

  In the heat exchange pipe of 1) above, if A <0.558, the liquid retention performance in the passage of the heat exchange pipe due to the capillary effect is insufficient, and the heat exchange pipe is used with its length direction directed vertically. In the refrigeration cycle provided with the evaporator, when the compressor is turned off, the refrigerant flows out from the passage of the heat exchange pipe in a short time, and the discharge temperature of the air passing through the evaporator rises rapidly. In addition, when 1.235 <A, the liquid retention performance in the passage of the heat exchange tube due to the capillary effect is improved, and the refrigeration provided with an evaporator in which the heat exchange tube is used with its length direction directed vertically. In the cycle, when the compressor is turned off, the refrigerant can be prevented from flowing out of the passage of the heat exchange pipe in a short time, but the cooling performance is lowered when the compressor is turned on.

2) A heat exchange pipe having a flat shape and a plurality of passages arranged in the width direction,
A heat exchange tube that satisfies the relationship of 0.35 ≦ Dh ≦ 1.0 when the equivalent diameter is Dh (mm).

  In the heat exchange pipe of the above 2), as is known, the equivalent diameter is an equivalent diameter of a pipe line when a heat exchange pipe having a plurality of non-circular passages is regarded as a circular pipe having one pipe line. Meaning, defined by:

  Dh = (4Ac) / Pi, where Ac is the sum of the passage cross-sectional areas of the plurality of passages, and Pi is the sum of the inner circumferential lengths of the plurality of passages.

  In the heat exchange pipe of 2) above, if Dh <0.35, the liquid retention performance in the passage of the heat exchange pipe due to the capillary effect is improved, and the heat exchange pipe is used with its length direction oriented vertically. In a refrigeration cycle equipped with an evaporator, when the compressor is turned off, the refrigerant can be prevented from flowing out of the passage of the heat exchange pipe in a short time, but the cooling performance when the compressor is turned on descend. In addition, if 1.0 <Dh, the liquid retention performance in the passage of the heat exchange tube due to the capillary effect is insufficient, and the refrigeration provided with an evaporator in which the heat exchange tube is used with its length direction directed vertically. In the cycle, when the compressor is turned off, the refrigerant flows out of the passage of the heat exchange pipe in a short time, the discharge temperature of the air passing through the evaporator rises rapidly, and the cooling when the compressor is turned on Performance is also reduced.

  3) The heat as described in 1) or 2) above, wherein ridges extending in the length direction of the passage are formed on the inner peripheral surface of each passage excluding two passages located at both ends in the width direction among all passages. Exchange tube.

  4) The heat exchange tube according to 3) above, wherein the number of ridges formed on the inner peripheral surface of each passage is two or more.

  5) The above-mentioned 1 in which the cross-sectional shape of each passage excluding two passages located at both ends in the width direction out of all the passages is a square, and the corner portion R of the cross-sectional square passage is 0.1 mm or less. ) Or 2).

  6) Two flat walls that are parallel to each other, both side walls that straddle both side edges of both flat walls, and that straddle both flat walls between both side walls and extend in the length direction of both flat wall portions The heat exchange tube according to any one of 1) to 5), wherein the heat exchange tube is formed of an extruded profile having a partition wall that partitions adjacent passages.

7) Two flat walls parallel to each other, both side walls provided across both side edges of both flat walls, and between both side walls, extending over both flat walls and extending in the length direction of both flat walls And a partition wall that partitions adjacent passages,
Two flat wall forming portions that form a flat wall, a connecting portion that connects both flat wall forming portions and one side wall, and a side edge opposite to the connecting portion in each flat wall forming portion, Side wall ridges that are integrally provided so as to protrude from the flat wall forming portion and that form the other side wall, and are integrally provided on each flat wall forming portion so as to protrude in the same direction as the side wall ridges. One metal plate provided with a plurality of partition wall ridges is formed by being bent into a hairpin shape at the connecting portion, the side wall ridges are butted together and brazed to each other, and at least The heat exchange tube according to any one of 1) to 5) above, wherein a partition wall is formed by the partition wall protrusions of any one of the flat wall forming portions.

  8) The heat exchange tube according to 7) above, wherein the partition wall is formed by abutment of the projections for partition walls of both flat wall forming portions and brazing each other.

  9) Of the two partition wall ridges forming each partition wall, a groove is formed on the tip surface of one partition wall ridge, into which the tip of the other partition wall ridge fits. 8) The heat exchange tube as described.

10) Two flat walls that are parallel to each other, both side walls that straddle both side edges of both flat walls, and that straddle both flat walls between both side walls and extend in the length direction of both flat wall portions And a partition wall that partitions adjacent passages,
For a side wall formed by bending one metal plate, one side wall is formed so as to project to the other flat wall side, continuing to one side edge of one flat wall, and facing the refrigerant passage Having a ridge, the other side wall is formed to be continuous with the other side edge of the other flat wall and project to the one flat wall side, and has a ridge for the side wall facing the refrigerant passage, A corrugated partition wall forming portion is integrally formed between the tip of the side wall ridge on the side wall and the tip of the side ridge on the other side wall, and the partition wall forming portion is one flat wall. The heat exchanging tube according to 1) or 2), comprising a wave crest portion brazed to the other flat wall, a wave bottom portion brazed to the other flat wall, and a connecting portion that connects the wave crest portion and the wave bottom portion and serves as a partition wall. .

11) A plurality of refrigerant heat passages having a plurality of flat heat exchange tubes arranged in the front-rear direction and spaced in the left-right direction and extending in the up-down direction, the heat exchange tubes being arranged in the width direction An evaporator having
An evaporator that satisfies the relationship of 0.558 ≦ A ≦ 1.235, where A is a value obtained by dividing the number of refrigerant passages of the heat exchange tube by the width in the front-rear direction of the heat exchange tube.

12) A plurality of refrigerant passages having a plurality of flat heat exchange tubes arranged in the front-rear direction and spaced in the left-right direction and extending in the up-down direction, the heat exchange tubes being arranged in the width direction An evaporator having
An evaporator that satisfies the relationship of 0.35 ≦ Dh ≦ 1.0, where Dh is the equivalent diameter of the heat exchange tube.

  13) On the inner peripheral surface of each refrigerant passage excluding two refrigerant passages located at both ends in the width direction among all the refrigerant passages of the heat exchange pipe, a ridge extending in the length direction of the refrigerant passage is formed. The evaporator according to 11) or 12).

  14) The evaporator according to 13) above, wherein the number of ridges formed on the inner peripheral surface of each passage of the heat exchange pipe is 2 or more.

  15) The cross-sectional shape of each refrigerant passage excluding two refrigerant passages located at both ends in the width direction of all the refrigerant passages of the heat exchange pipe is square, and R at the corner of the transverse refrigerant passage is The evaporator according to 11) or 12) above, which is 0.1 mm or less.

  16) A heat exchange pipe is provided between two flat walls parallel to each other, both side walls provided across both side edges of the two flat walls, and between both side walls and between the two flat walls. The evaporator according to any one of the above 11) to 15), which is formed of an extruded shape member that includes a partition wall that extends in the length direction and partitions adjacent passages.

17) A heat exchange pipe is provided between two flat walls facing each other, both side walls provided across both side edges of the two flat walls, and between both side walls and between the two flat walls. A partition wall that extends in the length direction and partitions adjacent passages,
The heat exchange pipe has two flat wall forming portions that form flat walls, a connecting portion that connects both flat wall forming portions and forms one side wall, and a side opposite to the connecting portion in each flat wall forming portion. Side wall ridges that are integrally provided to protrude from the flat wall forming portion and that form the other side wall, and that each flat wall forming portion protrudes in the same direction as the side wall ridges. A single metal plate having a plurality of partition wall projections provided integrally is bent into a hairpin shape at the connecting portion, and the side wall projections are butted together and brazed to each other. The evaporator according to any one of the above 11) to 15), wherein the partition wall is formed by a projection for the partition wall of at least one of the flat wall forming portions.

  18) The evaporator according to 17) above, wherein the heat exchange pipe is formed by brazing the partition walls with the partition wall protrusions of the flat wall forming portions being abutted against each other.

  19) Of the two partition wall ridges forming each partition wall, a concave groove is formed on the tip surface of one partition wall ridge, into which the tip of the other partition wall ridge fits. 18) The evaporator described.

20) A heat exchange pipe is provided between two flat walls parallel to each other, both side walls provided across both side edges of the two flat walls, and between the two side walls. A partition wall that extends in the length direction and partitions adjacent passages,
The heat exchange tube is formed by bending one metal plate, and one side wall is formed to be continuous with one side edge of one flat wall and project to the other flat wall side, and the refrigerant passage A side wall ridge that faces the refrigerant passage and has a side wall ridge facing the inside, the other side wall being connected to the other side edge of the other flat wall and projecting to the one flat wall side. And a corrugated partition wall forming portion is integrally formed between the tip of the side wall ridge on one side wall and the tip of the side wall ridge on the other side wall. 11) to 15), comprising a wave crest brazed to one flat wall, a wave bottom brazed to the other flat wall, and a connecting portion that connects the wave crest and the wave bottom and serves as a partition wall. The evaporator according to any one of the above.

  21) A refrigerant inlet / outlet header tank having a refrigerant inlet header portion and a refrigerant outlet header portion arranged side by side in the front-rear direction, and disposed below the refrigerant inlet / outlet header tank and facing the refrigerant inlet header portion A refrigerant turn header tank having a second intermediate header portion facing the first intermediate header portion and the refrigerant outlet header portion and communicating with the first intermediate header tank; and a heat exchange core portion formed between the header tanks. The heat exchange core portion is arranged adjacent to the heat exchange tube group including a plurality of heat exchange tubes arranged at intervals in the length direction of both header tanks and having both end portions connected to both header tanks. And two or more heat exchange tube groups arranged side by side in the ventilation direction between the header tanks, the refrigerant inlet header portion, the first intermediate header portion, and the Evaporator according to any of the above 11) to 20) of the heat exchange tubes of the fine outlet header and at least one heat exchange tube group, respectively to the second intermediate header section are connected.

  22) A refrigeration cycle comprising a compressor, a condenser, and an evaporator, wherein the evaporator is the evaporator according to any one of the above 11) to 21).

  23) A vehicle equipped with the refrigeration cycle described in 22) above as a car air conditioner.

  According to the heat exchange pipes 1) and 2), the liquid retention performance in the passage of the heat exchange pipe is improved by the capillary effect. Therefore, in a refrigeration cycle provided with an evaporator in which the heat exchanger tube is used with its length direction oriented vertically, even when the compressor is turned off, the liquid-phase refrigerant is removed from the heat exchanger tube by the capillary effect. Since the liquid phase refrigerant is held in the passage for a relatively long time, the liquid refrigerant is prevented from flowing out of the passage of the heat exchange pipe in a short time. And even after the compressor is turned off, while the liquid refrigerant remains in the passage of the evaporator heat exchange pipe, heat exchange between the remaining liquid refrigerant and the air passing through the evaporator Since this is continuously performed, it is possible to suppress a rapid rise in the discharge temperature. As a result, when the compressor is controlled based on the discharge air temperature of the evaporator, the high temperature side set temperature can be set lower than that of the evaporator described in Patent Document 1, and the compressor is turned on and off when the compressor is on and off. The temperature difference of the blown-out air can be reduced, and the comfort in the passenger compartment of the automobile is improved. And since the rapid rise of the discharge temperature after a compressor turns off can be suppressed, when controlling a compressor based on the discharge temperature of an evaporator, high temperature side preset temperature is set to the evaporator of patent document 1 description. Even when the temperature is set lower than the high temperature side set temperature, the compressor ON / OFF cycle can be made the same as that of the compressor using the evaporator described in Patent Document 1, so that the evaporator described in Patent Document 1 is used. The compressor does not turn on and off frequently, and does not adversely affect the fuel consumption of the car.

  According to the heat exchange pipes 3) to 5), the effect of holding the liquid-phase refrigerant in the passage of the heat exchange pipe is further improved by the capillary effect.

  According to the evaporators 11) and 12), the liquid retention performance in the passage of the heat exchange tube due to the capillary effect is improved. Therefore, in the refrigeration cycle provided with this evaporator, even when the compressor is turned off, the liquid phase refrigerant is held in the passage of the heat exchange pipe for a relatively long time due to the capillary effect. It is prevented from flowing out of the passage of the heat exchange pipe in a short time. And even after the compressor is turned off, while the liquid refrigerant remains in the passage of the evaporator heat exchange pipe, heat exchange between the remaining liquid refrigerant and the air passing through the evaporator Since this is continuously performed, it is possible to suppress a rapid rise in the discharge temperature. As a result, when the compressor is controlled based on the discharge air temperature of the evaporator, the high temperature side set temperature can be set lower than that of the evaporator described in Patent Document 1, and the compressor is turned on and off when the compressor is on and off. The temperature difference of the blown-out air can be reduced, and the comfort in the passenger compartment of the automobile is improved. And since the rapid rise of the discharge temperature after a compressor turns off can be suppressed, when controlling a compressor based on the discharge temperature of an evaporator, high temperature side preset temperature is set to the evaporator of patent document 1 description. Even when the temperature is set lower than the high temperature side set temperature, the compressor ON / OFF cycle can be made the same as that of the compressor using the evaporator described in Patent Document 1, so that the evaporator described in Patent Document 1 is used. The compressor does not turn on and off frequently, and does not adversely affect the fuel consumption of the car.

  According to the evaporators 13) to 15), the effect of holding the liquid-phase refrigerant in the passage of the heat exchange tube is further improved by the capillary effect.

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

  1 and 2 show the overall configuration of the evaporator, and FIGS. 3 to 11 show the configuration of the main part of the evaporator.

  As shown in FIGS. 1 to 3, the evaporator (20) is disposed between an aluminum refrigerant inlet / outlet header tank (22) and an aluminum refrigerant turn header tank (23) that are spaced apart in the vertical direction. Is provided with a heat exchange core section (21).

  The refrigerant inlet / outlet tank (22) includes a refrigerant inlet header portion (24) located on the front side (downstream side in the ventilation direction), a refrigerant outlet header portion (25) located on the rear side (upstream side in the ventilation direction), And a connecting portion (26) for connecting and integrating the header portions (24) and (25) to each other. An aluminum refrigerant inlet pipe (27) is connected to the refrigerant inlet header (24) of the refrigerant inlet / outlet tank (22), and an aluminum refrigerant outlet pipe (28) is connected to the refrigerant outlet header (25). Yes.

  The refrigerant turn header tank (23) includes a refrigerant inflow side intermediate header portion (30) (first intermediate header portion) located on the front side and a refrigerant outflow side intermediate header portion (31) (second intermediate point) located on the rear side. Header portion) and a connecting portion (32) for connecting and integrating the header portions (30) and (31) to each other, and the header portions (30) and (31) and the connecting portion (32) provide drainage. A ridge (33) is formed.

  The heat exchange core section (21) includes a plurality of rows of heat exchange pipe groups (35) including a plurality of heat exchange pipes (34) arranged in parallel at intervals in the left-right direction. Are arranged in two rows, and the ventilation gap between adjacent heat exchange pipes (34) of each heat exchange pipe group (35) and the heat exchange pipes (34) at the left and right ends of each heat exchange pipe group (35). Corrugated fins (36) are arranged on the outside and brazed to the heat exchange pipe (34), and further, aluminum side plates (37) are arranged on the outside of the corrugated fins (36) on both left and right ends, respectively. It is composed by brazing to 36). Then, the upper and lower ends of the heat exchange pipe (34) of the front heat exchange pipe group (35) are connected to the refrigerant inlet header part (24) and the refrigerant inflow side intermediate header part (30) to become the forward side refrigerant circulation part. Yes. The upper and lower ends of the heat exchange pipe (34) of the rear heat exchange pipe group (35) are connected to the refrigerant outlet header part (25) and the refrigerant outflow side intermediate header part (31) to form a return side refrigerant circulation part. Yes. Then, the refrigerant inlet header (24) and the refrigerant outlet are formed by the refrigerant inflow side intermediate header (30), the refrigerant outflow side intermediate header (31), and the heat exchange pipe (34) of the front and rear heat exchange pipe groups (35). A refrigerant circulation path is formed through the header section (25).

  The heat exchange pipe (34) is made of a bare material formed of an aluminum extruded profile, and, as shown in FIG. 4, has a flat shape having a plurality of refrigerant passages (34a) aligned in the width direction with the width direction directed in the front-rear direction. Two flat left and right walls (341) and (342) facing each other, and both front and rear side walls (343) and (344) provided across both side edges of the left and right walls (341) and (342) The refrigerant passages (34a) provided between the front and rear side walls (343) and (344) so as to straddle the left and right walls (341) and (342) and extending in the length direction of the left and right walls (341) and (342) And a partition wall (345) for partitioning each other. On the inner peripheral surface of each refrigerant passage (34a) excluding two refrigerant passages (34a) located at both ends in the width direction of all the refrigerant passages (34a) of the heat exchange pipe (34), the refrigerant passage (34a) Two or more, four ridges (346) extending in the length direction are formed here. That is, in each refrigerant passage (34a) excluding two refrigerant passages (34a) located at both ends in the width direction of all the refrigerant passages (34a) of the heat exchange pipe (34), both left and right walls (341) (342 ) On the inner surface of each of the two protrusions (346) are formed at intervals in the front-rear direction. Further, the cross-sectional shape of each refrigerant passage (34) excluding two refrigerant passages (34a) located at both ends in the width direction of all the refrigerant passages (34a) is a square shape, R of the corner portion (34b) of 34a) is 0.1 mm or less. The cross-sectional shape of the front and rear side walls (342) and (343) of the heat exchange pipe (34) is an arc shape whose central portion protrudes outward. The front heat exchange pipe (34) and the rear heat exchange pipe (34) are arranged to be at the same position in the left-right direction. The front heat exchange pipe (34) communicates with the refrigerant inlet header section (24) and the refrigerant inflow side intermediate header section (30), and the rear heat exchange pipe (34) communicates with the refrigerant outlet header section (25) and It communicates with the refrigerant outflow side intermediate header (31).

  In this heat exchange pipe (34), when the value obtained by dividing the number of refrigerant passages (34a) by the width (W) in the front-rear direction is A (pieces / mm), a relationship of 0.558 ≦ A ≦ 1.235 Meet. Further, when the equivalent diameter of the heat exchange pipe (34) is Dh (mm), the relationship of 0.35 ≦ Dh ≦ 1.0 is satisfied. The heat exchange pipe (34) has a case where only one of the two conditions is satisfied or a case where both are satisfied.

  The corrugated fin (36) is formed in a corrugated shape using an aluminum brazing sheet having a brazing filler metal layer on both sides, from the wave top, the wave bottom and the flat horizontal connecting portion connecting the wave top and the wave bottom. Thus, a plurality of louvers are formed in the connecting portion side by side in the front-rear direction. The corrugated fin (36) is shared by the front and rear heat exchange tubes (34) constituting the front and rear heat exchange tube group (35), and the width in the front-rear direction is equal to the front edge of the front heat exchange tube (34). The distance from the rear edge of the rear heat exchange pipe (34) is substantially equal. The wave crest and wave bottom of the corrugated fin (36) are brazed to the front and rear heat exchange tubes. The front edge of the corrugated fin (36) protrudes slightly forward from the front edge of the front heat exchange pipe (34).

  As shown in FIGS. 3, 5 and 6, the refrigerant inlet / outlet header tank (22) is a plate formed of an aluminum brazing sheet having a brazing filler metal layer on both sides and to which all heat exchange pipes (34) are connected. Aluminum brazing comprising a first member (38) having a shape, a second member (39) made of a bare material formed from an extruded aluminum material and covering the upper side of the first member (38), and a brazing material layer on both sides It consists of aluminum closing members (41) (42) formed from a sheet and brazed to both ends of both members (38) (39), and on the outer surface of the right closing member (42), the refrigerant inlet header (24 ) And a joint plate (43) made of aluminum that is long in the front-rear direction so as to straddle the refrigerant outlet header portion (25). A refrigerant inlet pipe (27) and a refrigerant outlet pipe (28) are connected to the joint plate (43).

  The first member (38) includes a first bulging first header forming portion (44) that forms a lower portion of the refrigerant inlet header portion (24) and a lower bulging that forms a lower portion of the refrigerant outlet header portion (25). A second header forming portion (45), a rear edge portion of the first header forming portion (44) and a front edge portion of the second header forming portion (45), and a lower portion of the connecting portion (32) And a connecting wall (46). A plurality of pipe insertion holes (47) that are long in the front-rear direction are formed in both header forming portions (44), (45) at intervals in the left-right direction. The pipe insertion holes (47) of both header forming portions (44) and (45) are at the same position in the left-right direction. The upper end portions of the heat exchange tubes (34) of both the front and rear heat exchange tube groups (35) of the heat exchange core portion (21) are inserted into the tube insertion holes (47) of both header forming portions (44) (45), The first member (38) is brazed to the first member (38) using the brazing material layer of the first member (38), whereby the upper end of the heat exchange pipe (34) of the front heat exchange pipe group (35) is connected to the refrigerant inlet. An upper end portion of the heat exchange pipe (34) of the rear heat exchange pipe group (35) is connected to the header section (24) in communication with the refrigerant outlet header section (25). A plurality of drainage through holes (48) that are long in the left-right direction are formed in the connecting wall (46) at intervals in the left-right direction. In addition, a plurality of fixing through holes (49) are formed in the connecting wall (46) of the first member (50) at intervals in the left-right direction so as to be shifted from the drain through holes (48). Has been.

  The second member (39) includes an upper bulging first header forming part (51) that forms the upper part of the refrigerant inlet header part (24), and an upper bulging that forms the upper part of the refrigerant outlet header part (31). A second header forming part (52) having a shape, a rear edge of the first header forming part (51) and a front edge of the second header forming part (52), and the first member (38) The connecting wall (53) is brazed to the connecting wall (46) to form the upper part of the connecting portion (26). The first header forming part (51) is a horizontal part that integrally connects the lower ends of both front and rear walls (51a) and partitions the refrigerant inlet header part (24) into two upper and lower spaces (24A) and (24B). It has a diversion control wall (51b) in the inlet header section. The second header forming portion (52) integrally connects the lower ends of the front and rear walls (52a) at the same height as the inlet header diversion control wall (51b) and in the refrigerant outlet header portion (25). Is divided into two upper and lower spaces (25A) and (25B).

  A notch (50) is formed from the left end of the flow dividing control wall (51b) in the inlet header portion of the second member (39). In addition, a diversion adjusting hole (60) is formed in a penetrating manner in a portion near the notch (50) and a portion near the right end of the diversion control wall (51b) in the inlet header portion. A plurality of oblong coolant passage holes (54A) (54B) that are long in the left-right direction are formed in the left and right ends of the rear portion of the second header member (39) in the outlet header inner flow control wall (52b). It is formed in a penetrating manner with an interval in the direction. The length of the oval refrigerant through hole (54A) at the center is shorter than the length of the other oval refrigerant through hole (54B) and is located between the adjacent heat exchange tubes (34).

  In the connecting wall (53) of the second member (39), a drainage through hole (55) that is long in the left-right direction is formed at a position matching the drainage through hole (48) of the first member (38). A plurality of protrusions (56) that are respectively fitted into the fixing through holes (49) are formed at positions corresponding to the fixing through holes (49) of one member (38). In the first member (38) and the second member (39), the protrusion (56) is inserted into the fixing through hole (49) and caulked so that both members (38) and (39) are temporarily fixed. In the state, using the brazing material layer of the first member (38), the front side edge portions of the first header forming portions (44) and (51) of both members (38) and (39) are connected to each other, and the second header forming portion ( 45) The rear edge portions of (52) and the connecting portions (46) (53) are brazed.

  A hollow inlet header portion main body (240) having both ends opened by the first header forming portion (44) of the first member (38) and the first header forming portion (51) of the second member (39). A hollow outlet header main body (both ends open) by the second header forming portion (45) of the second member (39) and the second header forming portion (52) of the second member (39). 250) is formed.

  The left closing member (41) includes a front cap (41a) for closing the left end opening of the inlet header body (240) and a rear cap (41b) for closing the left end opening of the outlet header body (250). Integrated through (41c). The front cap (41a) of the closing member (41) is integrally formed with a right protrusion (57) that is fitted into the inlet header body (240), and the rear cap (41b) is also provided with an outlet header. The upper right protrusion (58) that fits into the space above the flow dividing control wall (52b) of the head part body (250), and the bottom that fits into the space below the flow dividing control wall (52b). The side right protrusion (59) is integrally formed with a space in the vertical direction. Further, engaging claws (61) projecting to the right and engaging with both members (38) (39) in the arc-shaped portions between the front and rear side edges and the upper and lower edges of the left closing member (41). ) Are integrally formed. The left closing member (41) is brazed to both members (38) and (39) using its own brazing material layer. Then, the left end opening of the notch (50) of the inlet header diversion control wall (51b) is closed by the front cap (41a) of the left closing member (41), whereby both the upper and lower spaces of the inlet header portion (24) ( A communication hole (70) is formed in the left end portion so that 24A) and (24B) communicate with each other. Here, the communication hole (70) is formed by closing the left end opening of the notch (50) by the left cap (18), but instead of this, the notch is not formed, and the inside of the inlet header portion is formed. A communication hole may be provided by forming a through hole in the left end portion of the flow dividing control wall (51b).

  The right closing member (42) includes a front cap (42a) that closes the right end opening of the inlet header body (240) and a rear cap (42b) that closes the right end opening of the outlet header body (250). Integrated through (42c). The front cap (42a) of the closing member (42) has an upper left protrusion (62) fitted into the space above the flow dividing control wall (51b) of the inlet header body (240), and a flow dividing control. The lower left protrusion (80) fitted into the space below the wall (51b) is integrally formed with a space in the vertical direction, and the rear cap (42b) has an outlet header main body. (250) The upper left protrusion (63) that fits in the space above the flow dividing control wall (52b), and the lower left that fits in the space below the flow dividing control wall (52b). The side protrusions (64) are integrally formed with a space in the vertical direction. A refrigerant inlet (66) is formed in the protruding end wall of the upper left protrusion (62) of the front cap (42a) of the right closing member (42), and the upper left protrusion (63) of the rear cap (42b) is also formed. A refrigerant outlet (67) is formed in the protruding end wall. Engaging claws (65) projecting to the left and engaging both members (38) and (39) on the arc-shaped portions between the front and rear side edges and the upper and lower edges of the right closing member (42) It is integrally formed.

  As shown in FIGS. 7-9, the 1st engagement male part (1) which protruded upwards in the center part of the front-back direction in the upper end of the connection part (42c) of a right side closing member (42) is integrally formed, Similarly, a second engaging male part (2) projecting downward is integrally formed at the center part in the front-rear direction at the lower end of the connecting part (42c). When the evaporator (20) is manufactured, the second engaging male part (2) protrudes to the right before the right closing member (42) is combined with the joint plate (43). The second engaging male part protruding rightward is indicated by (2A) (see the chain line in FIG. 9). Further, notches (3) are formed at both front and rear ends of the lower edge of the right closing member (42). The right closing member (42) is brazed to both members (38) and (39) using its own brazing material layer.

  The joint plate (43) includes a short cylindrical refrigerant inlet (68) that communicates with the refrigerant inlet (66) of the right closing member (42), and a short cylindrical refrigerant outlet (69) that also communicates with the refrigerant outlet (67). It has. The refrigerant inflow port (68) and the refrigerant outflow port (69) are each composed of a circular through hole and a short cylindrical part integrally formed so as to protrude rightward around the through hole.

  In the joint plate (21) between the refrigerant inlet (68) and the refrigerant outlet (69), a slit (4) for preventing a short circuit extending in the vertical direction is formed, and the slit (4) Substantially trapezoidal through-holes (5) and (6) are formed to be connected to the upper and lower ends. The upper part of the upper through hole (5) and the lower part of the lower through hole (6) of the joint plate (43) are U-shaped so as to protrude to the left (on the right closing member (42) side). And the first and second engaging female portions (7) and (8) are formed. The first engaging female portion (7) is inserted into the first engaging male portion (1) of the right closing member (42) from below and engaged with the first engaging female portion (7). At the same time, the second engaging female portion (8) is inserted through the second engaging male portion (2) of the right closing member (42) from above and engaged with the second engaging female portion (8). This prevents the joint plate (43) from moving in the left-right direction. The second engagement male part (2) of the right closing member (42) is bent downward after passing through the lower through hole (6) in a state of protruding to the right side shown by a chain line in FIG. The second engaging female portion (8) is inserted from above. Further, the first engaging female portion (7) is engaged with both front and rear side portions of the first engaging male portion (1) in the connecting portion (42c) of the closing member (42), whereby the joint plate ( 43) is prevented from moving downward. Furthermore, an engaging claw (9) projecting leftward is formed integrally with the front and rear ends of the lower edge of the joint plate (43), and the engaging claw (9) is formed on the right closing member (9). 42) engaged with the right closing member (42) in a state of being fitted in a notch (3) formed on the lower edge, thereby preventing the joint plate (43) from moving upward and forward and backward. Has been. As described above, the joint plate (43) is engaged with the closing member (42) so as to be prevented from moving in the left-right direction, the up-down direction, and the front-rear direction, and the brazing material layer of the closing member (42). Is used to braze the closing member (42).

  A reduced diameter portion formed at one end of the refrigerant inlet pipe (27) is inserted into the refrigerant inlet (68) of the joint plate (43) and brazed, and similarly to the refrigerant outlet (69), the refrigerant outlet pipe A reduced diameter portion formed at one end of (28) is inserted and brazed. Although not shown, an expansion valve mounting member is joined to the other ends of the refrigerant inlet pipe (27) and the refrigerant outlet pipe (28) so as to straddle both pipes (27) and (28).

  As shown in FIGS. 2, 3, 10 and 11, the refrigerant turn header tank (23) is formed of an aluminum brazing sheet having a brazing filler metal layer on both sides, and all the heat exchange tubes (34) are connected. Plate-shaped first member (73), a second member (74) made of a bare material formed from an extruded aluminum material and covering the lower side of the first member (73), and a brazing material layer on both sides An aluminum closing member (75) (76) formed of an aluminum brazing sheet having a right angle and brazed to both ends of both members (73) (74), and an outer surface of the right closing member (76) It consists of a communication member (77) made of aluminum bare material that is long in the front-rear direction and brazed so as to straddle the header section (30) and the refrigerant outflow side intermediate header section (31), and the refrigerant passes through the communication member (77). The inflow-side intermediate header (30) and the refrigerant outflow-side intermediate header (31) are at the right end. It is made to communicate with.

  The first member (73) forms an upper bulging first header forming part (78) that forms the upper part of the refrigerant inflow side intermediate header part (30) and the upper part of the refrigerant outflow side intermediate header part (31). Connecting the second bulging second header forming portion (79), the rear edge of the first header forming portion (78) and the front edge of the second header forming portion (79) 32) and a connecting wall (81) forming the upper part. Then, both side surfaces are provided by the inclined walls (78a) (79a) and the connecting walls (81) provided on the inner side in the front-rear direction of both header forming portions (78) (79) and inclined upward in the front-rear direction toward the upper side. A drainage basin (33) that is inclined outward in the front-rear direction toward the upper side is formed. A plurality of pipe insertion holes (82) that are long in the front-rear direction are formed in both header forming portions (78), (79) at intervals in the left-right direction. The pipe insertion holes (82) of both header forming portions (78) (79) are at the same position in the left-right direction. The end of the pipe insertion hole (82) on the connecting part (32) side, that is, the rear end of the pipe insertion hole (82) of the first header forming part (78) and the pipe insertion hole of the second header forming part (79) ( 82) are located on the inclined walls (78a) and (79a), respectively, so that the end of the pipe insertion hole (82) on the connection part (32) side is located on the side surface of the drainage basin (33). Yes. In addition, the front and rear direction outer portions of the pipe insertion holes (82) in both header forming portions (78) and (79) are connected to the outer ends of the pipe insertion holes (82) in the front-rear direction and away from the pipe insertion holes (82). A drainage groove (83) gradually downward is formed. The lower end portions of the heat exchange pipes (34) of the front and rear heat exchange pipe groups (35) of the heat exchange core part (21) are inserted into the pipe insertion holes (82) of both header forming parts (78) (79), The first member (73) is brazed to the first member (73) using the brazing material layer of the first member (73), so that the lower end portion of the heat exchange pipe (34) of the front heat exchange pipe group (35) flows into the refrigerant. The lower end portion of the heat exchange pipe (34) of the rear heat exchange pipe group (35) is connected to the side intermediate header part (30) in communication with the refrigerant outflow side intermediate header part (31). A plurality of drainage through holes (84) elongated in the left-right direction are formed in the connecting wall (81) of the first member (73) at intervals in the left-right direction. In addition, a plurality of fixing through holes (85) are formed in the connecting wall (81) of the first member (73) at intervals in the left-right direction so as to be shifted from the drain through holes (84). Has been. The first member (73) has the same shape as the first member (38) of the refrigerant inlet / outlet header tank (22), and both the members (73) and (38) are arranged upside down.

  The second member (74) forms a first bulging first header forming portion (86) that forms a lower portion of the refrigerant inflow side intermediate header portion (30), and a lower portion of the refrigerant outflow side intermediate header portion (31). The second bulge-shaped second header forming portion 87 and the header forming portions 86, 87 are connected to each other and brazed to the connecting wall 81 of the first member 73 so that the connecting portion ( And a connecting wall (88) forming 32). The second header forming portion (87) integrally connects the upper end portions of the front and rear walls (87a) and partitions the refrigerant outflow side intermediate header portion (31) into two upper and lower spaces (31A) and (31B). A horizontal flow control wall (87b). A plurality of circular coolant passage holes (89) are formed in a penetrating manner at intervals in the left-right direction at a portion of the shunt control wall (87b) on the rear side of the center portion in the front-rear direction. The distance between adjacent circular refrigerant passage holes (89) gradually increases as the distance from the right end portion increases. Note that the intervals between adjacent circular refrigerant passage holes (89) may all be equal. In the connecting wall (88) of the second member (74), a drainage through hole (91) that is long in the left-right direction is formed at a position matching the drainage through hole (84) of the first member (73). Protrusions (92) that protrude upward and are inserted through the fixing through holes (85) are formed at positions corresponding to the fixing through holes (85) of one member (73). In the first member (73) and the second member (74), the protrusion (92) is inserted into the fixing through hole (85) and caulked so that both members (73) and (74) are temporarily fixed. In this state, using the brazing material layer of the first member (73), the front edge portions of the first header forming portions (78) and (86) of both members (73) and (74) are connected to each other, and the second header forming portion ( 79) (87) rear edge portions and connecting portions (81) (88) are brazed. The second member (74) is the first member of the refrigerant inlet / outlet header tank (22) except for the shape and position of the refrigerant passage holes (89), (54A), (54B) and the presence / absence of the flow dividing control wall (52b). The shape is the same as that of the member (39), and both the members (74) (39) are arranged upside down. Both members (74) and (39) are formed from the same extruded profile.

  And the hollow refrigerant inflow side intermediate header part main body which the both ends opened by the 1st header formation part (78) of the 1st member (73) and the 1st header formation part (86) of the 2nd member (74) (300) is formed, and the hollow refrigerant outflow is opened at both ends by the second header forming portion (79) of the second member (74) and the second header forming portion (87) of the second member (74). A side intermediate header body (310) is formed.

  The left closing member (75) includes a front cap (75a) for closing the left end opening of the refrigerant inflow side intermediate header part main body (300), and a rear cap for closing the left end opening of the refrigerant outflow side intermediate header part main body (310) ( 75b) is integrated, and the front cap (75a) is integrally formed with a right protrusion (93) fitted into the refrigerant inflow side intermediate header body (300). The cap (75b) includes an upper right protrusion (94) fitted into the space above the flow dividing control wall (87b) of the refrigerant outflow side intermediate header section main body (310), and a flow dividing control wall (87b). A lower right protrusion (95) fitted into the lower space is integrally formed with a space in the vertical direction. Further, in the arc-shaped portion between the front and rear side edges and the upper edge and the lower edge of the left closing member (75), the engaging claws (100) projecting to the right and engaging with both members (73) (74). ) Are integrally formed. The left closing member (75) is brazed to both members (73) and (74) using its own brazing material layer.

  The right closing member (76) includes a front cap (76a) for closing the right end opening of the refrigerant inflow side intermediate header part main body (300) and a rear cap for closing the right end opening of the refrigerant outflow side intermediate header part main body (310) ( 76b) is integrally formed, and the front cap (76a) is integrally formed with a left protrusion (96) that is fitted into the refrigerant inflow side intermediate header body (300). The cap (76b) includes an upper left protrusion (97) fitted into the space above the flow dividing control wall (87b) of the refrigerant outflow side intermediate header section main body (310), and a flow dividing control wall (87b). A lower left projecting portion (98) fitted into the lower space is integrally formed with a space in the vertical direction. Further, in the arc-shaped portion between the front and rear side edges and the upper edge and the lower edge of the right closing member (76), the engaging claws (99) projecting to the left and engaging the both members (73) (74). ) Are integrally formed. Also, the engaging claws (104) projecting rightward and bent downward at the front and rear end portions of the upper edge of the right closing member (76) and engaged with the upper edge portion of the communication member (77). Is formed integrally, and protrudes rightward and bent upward at the center in the front-rear direction of the lower edge of the right closing member (76) and is engaged with the lower edge of the communication member (77). The engaging claw (104) is integrally formed. On the protruding end wall of the left protruding portion (96) of the front cap (76a) of the right closing member (76), a refrigerant outlet (101) for allowing the refrigerant to flow out from the refrigerant inflow side intermediate header portion (30) is formed, Similarly, the refrigerant is placed in the space (31B) below the branching control wall (87b) of the refrigerant outflow side intermediate header (31) on the protruding end wall of the lower left protrusion (98) of the rear cap (76b). A refrigerant inlet (102) is formed to allow the refrigerant to flow in. Further, in the lower part of the peripheral edge of the refrigerant inlet (102) in the lower left protruding part (98) of the rear cap (76b), the refrigerant outlet side intermediate header part (31) is inclined upward inward. Alternatively, a curved guide portion (103) is formed integrally. The guide part (103) causes the refrigerant flowing into the space (31B) below the flow dividing control wall (87b) of the refrigerant outflow side intermediate header part (31) to flow upward (to the flow dividing control wall (87b) side). invite. The right closing member (76) is brazed to both members (73) (74) using its own brazing material layer.

  The communication member (77) is formed by pressing an aluminum bear material, and is a plate having the same shape and size as the right closing member (76) when viewed from the right, and its peripheral portion is The outer surface of the right closing member (76) is brazed using the brazing material layer of the right closing member (76). The communication member (77) is formed with an outward bulging portion (105) so as to allow the refrigerant outlet (101) and the refrigerant inlet (102) of the right closing member (76) to pass therethrough. The inside of the outward bulging portion (105) serves as a communication path through which the refrigerant outlet (101) and the refrigerant inlet (102) of the right closing member (76) are passed. In addition, notches (106) into which the engaging claws (104) of the right closing member (76) are fitted are formed in the front and rear end portions of the upper edge of the communication member (77) and the center portion of the lower edge in the front-rear direction. ing.

  The evaporator (20) described above is manufactured by combining all the parts except the inlet pipe (27) and the outlet pipe (28) and brazing them together.

  The evaporator (20) constitutes a refrigeration cycle using a chlorofluorocarbon refrigerant together with a fixed capacity compressor and a condenser as a refrigerant cooler, and is mounted on a vehicle such as an automobile as a car air conditioner.

  In the evaporator (20) described above, when the fixed capacity compressor is turned on, the gas-liquid mixed phase two-phase refrigerant that has passed through the compressor, the condenser, and the expansion valve flows from the refrigerant inlet pipe (27) to the refrigerant inlet of the joint plate (43). (68) and through the refrigerant inlet (66) of the front cap (42a) of the right closing member (42) into the upper space (24A) of the refrigerant inlet header portion (24) of the refrigerant inlet / outlet tank (22). . The refrigerant that has entered the upper space (24A) of the refrigerant inlet header (24) flows to the left, enters the lower space (24B) through the communication hole (70), and passes through the flow dividing adjustment hole (60). Enter the lower space (24B).

  The refrigerant entering the lower space (24B) is divided and flows into the refrigerant passage (34a) of the heat exchange pipe (34) of the front heat exchange pipe group (35). The refrigerant that has flowed into the refrigerant passage (34a) of the heat exchange pipe (34) flows downward in the refrigerant passage (34a) and into the refrigerant inflow side intermediate header (30) of the refrigerant turn header tank (23). enter. The refrigerant that has entered the refrigerant inflow side intermediate header (30) flows to the right, the refrigerant outlet (101) of the front cap (76a) of the right closing member (76), and the outward expansion of the communication member (77). The lower space (31B) of the refrigerant outflow side intermediate header section (31) by turning through the communication path in the section (105) and the refrigerant inlet (102) of the rear cap (76b) to change the flow direction. Get inside.

  The refrigerant that has entered the lower space (31B) of the refrigerant outflow side intermediate header (31) flows to the left, passes through the circular refrigerant passage hole (89) of the flow dividing control wall (87b), and enters the upper space (31A). It enters, splits, and flows into the refrigerant passages (34a) of all the heat exchange tubes (34) on the rear side. At this time, the refrigerant is guided to the guide part (103) and flows to the left side upward, that is, inward of the lower space (31B) toward the diversion control wall (87b), and as a result, the diversion control wall ( In combination with the fact that the interval between adjacent circular refrigerant passage holes (89) formed in 87b) gradually increases as the distance from the right end increases, the upper space (89) passes through the refrigerant passage hole (89). The distribution in the left-right direction of the refrigerant flowing into 31A) is made uniform as compared with the case where there is no guide portion (103). Therefore, the refrigerant is likely to be evenly divided into the heat exchange pipe (34) connected to the refrigerant outflow side intermediate header part (31), and the distribution of the refrigerant in the heat exchange core part (21) is less likely to occur. The temperature of the air passing through the heat exchange core part (21) is also made uniform, and the heat exchange performance is improved.

  The refrigerant flowing into the refrigerant passage (34a) of the heat exchange pipe (34) changes the flow direction and flows upward in the refrigerant passage (34a) to enter the lower space (25B) of the refrigerant outlet header (25). And enters the upper space (25A) through the oblong refrigerant passage holes (54A) (54B) of the flow dividing control wall (52b).

  Next, the refrigerant that has entered the upper space (25A) of the refrigerant outlet header (25) flows into the refrigerant outlet (67) of the rear cap (42b) of the right closing member (42) and the refrigerant outlet of the joint plate (43). It passes through (69) and flows out to the refrigerant outlet pipe (28).

  While the refrigerant flows through the refrigerant passage (34a) of the front heat exchange pipe (34) and the refrigerant passage (34a) of the rear heat exchange pipe (34), the ventilation gap of the heat exchange core section (21) The refrigerant exchanges heat with the air passing through and flows out as a gas phase.

  When the fixed capacity compressor is off, the liquid phase refrigerant remaining in the refrigerant passage (34a) of the heat exchange pipe (34) is effectively retained in the refrigerant passage (34a) by the capillary effect, so the liquid phase refrigerant is short. Outflow from the refrigerant passage (34a) of the heat exchange pipe (34) over time is prevented. And even after the compressor is turned off, while the liquid-phase refrigerant remains in the refrigerant passage (34a) of the heat exchange pipe (34) of the evaporator (20), the remaining liquid-phase refrigerant and the evaporator Since the heat exchange with the air passing through (20) is continuously performed, it is possible to suppress a rapid increase in the discharge temperature.

  The change in the air discharge temperature when the fixed capacity compressor of the car air conditioner using the evaporator (20) is turned on and off is shown by a solid line in FIG. As is clear from FIG. 12, when compared with the change in the discharge temperature when the fixed capacity compressor of the car air conditioner using the evaporator described in Patent Document 1 indicated by the chain line is turned on and off, in the case of the evaporator (20), the compressor The rise in temperature will be moderate after the is turned off. Therefore, when the compressor is controlled based on the discharge temperature of the evaporator (20), even if the high temperature side set temperature (T2) is set lower than the high temperature side set temperature (t2) of the evaporator described in Patent Document 1, the compressor Can be made the same as the compressor using the evaporator described in Patent Document 1. As a result, the temperature difference between the air blown into the vehicle compartment when the compressor is on and off can be reduced, and comfort in the vehicle compartment of the automobile is improved. Moreover, even if the high temperature side set temperature (T2) is lowered and the temperature difference from the low temperature side set temperature (T1) is reduced, the on / off cycle of the compressor should be the same as that of the evaporator described in Patent Document 1. Therefore, unlike the case of the evaporator described in Patent Document 1, the compressor is not frequently turned on and off, and the fuel consumption of the automobile is not adversely affected.

  Next, an example of an evaporator according to the present invention will be shown together with a comparative example.

Example 1
4, that is, the number of refrigerant passages (34a) is 11, and the number of ridges on the inner peripheral surface of each refrigerant passage (34a) excluding the refrigerant passages (34a) at both ends is four. An evaporator (20) using 34) was prepared.

Example 2
The configuration shown in FIG. 13 (a), that is, the number of refrigerant passages (34a) is 14, and the number of ridges (346) on the inner peripheral surface of each refrigerant passage (34a) excluding the refrigerant passages (34a) at both ends is four. An evaporator using a heat exchange tube (34A) was prepared.

Example 3
The configuration shown in FIG. 13B, that is, the number of refrigerant passages (34a) is 16, and the number of protrusions (346) on the inner peripheral surface of each refrigerant passage (34a) excluding the refrigerant passages (34a) at both ends is four. An evaporator using a heat exchange pipe (34B) was prepared.

Example 4
The configuration shown in FIG. 13C, that is, the number of refrigerant passages (34a) is 16, and the number of ridges (346) on the inner peripheral surface of each refrigerant passage (34a) excluding the refrigerant passages (34a) at both ends is four. An evaporator using a heat exchange tube (34C) was prepared.

Example 5
The configuration shown in FIG. 13D, that is, the number of refrigerant passages (34a) is 20, and the number of protrusions (346) on the inner peripheral surface of each refrigerant passage (34a) excluding the refrigerant passages (34a) at both ends is four. An evaporator using a heat exchange tube (34D) was prepared.

Comparative Example The configuration shown in FIG. 13 (e), that is, the number of refrigerant passages (34a) is 7, and the number of protrusions (346) on the inner peripheral surface of each refrigerant passage (34a) excluding the refrigerant passages (34a) at both ends. An evaporator using a heat exchange tube (34E) having a value of 4 was prepared.

  The heat exchange tubes (34) (34A) (34B) (34C) (34D) (34E) used in the evaporators of Examples 1 to 5 and the comparative example had a width (W) in the front-rear direction of 17 mm and a thickness in the left-right direction. The tube height (H) is 1.4 mm. Also, the total cross-sectional area of the plurality of refrigerant passages (34a) in each heat exchange pipe (34) (34A) (34B) (34C) (34D) (34E), the inner circumference of the cross-section of the plurality of refrigerant passages (34a) The total length, the equivalent diameter Dh of each heat exchange pipe (34) (34A) (34B) (34C) (34D) (34E), and the value A obtained by dividing the number of refrigerant passages (34a) by the width in the front-rear direction Each is shown in Table 1.

Evaluation Test The evaporators of Examples 1 to 5 and the comparative example were incorporated into a refrigeration cycle, and the cooling performance when the fixed capacity compressor was turned on was examined. Also, the liquid remaining in the refrigerant passage (34a) of the heat exchange pipes (34) (34A) (34B) (34C) (34D) (34E) after 5 seconds has passed since the fixed capacity compressor was turned off. The amount of phase refrigerant was examined. Further, after 5 seconds have passed since the fixed capacity compressor was turned off, it remains in the refrigerant passage (34a) of the heat exchange tubes (34) (34A) (34B) (34C) (34D) (34E). The time until the liquid phase refrigerant evaporated was examined. The results are shown in Table 1, and the relationship between the cooling performance and the amount of remaining liquid-phase refrigerant, the equivalent diameter Dh, and the number of refrigerant passages (34a) is shown in FIGS. 14 and 15, the solid line indicates the cooling performance, and the broken line indicates the amount of the liquid-phase refrigerant that remains. The cooling performance is expressed as a ratio when the cooling performance of Example 2 is set to 100%, and the heat exchange pipes (34) (34A) (34B) (5 seconds after the fixed capacity compressor is turned off). The amount of liquid-phase refrigerant remaining in the refrigerant passage (34a) of (34C), (34D) and (34E) is expressed as a ratio when the amount of Example 1 is 100%. Here, if the cooling performance is in the range of 95 to 100% indicated by the arrow Z in FIGS. 14 and 15, it has sufficient performance as a car air conditioner.

  As is apparent from Table 1, FIG. 14 and FIG. 15, in the heat exchange pipe used, the value A obtained by dividing the number of refrigerant passages by the width in the front-rear direction is 0.558 ≦ A ≦ 1.235 and the equivalent diameter. The cooling performance of the evaporators of Examples 1-5 satisfying the relationship of Dh 0.35 ≦ Dh ≦ 1.0 is superior to the cooling performance of the evaporator of the comparative example, and has sufficient performance as a car air conditioner. . Further, the amount of liquid-phase refrigerant remaining in the refrigerant passage of the heat exchange pipe when the compressor in the evaporator of Examples 1 to 5 is turned off is larger than that of the evaporator of the comparative example. As a result, as described above, the temperature difference between the air blown into the passenger compartment when the compressor is on and off can be reduced, and comfort in the passenger compartment of the automobile is improved.

  16 to 18 show modifications of the heat exchange tube. In addition, in description of the modification of the heat exchange pipe | tube described below, the upper side of each figure is left and the lower side is right.

  In FIG. 16 and FIG. 17, the heat exchange pipe (130) is a flat shape having a refrigerant passage (130a) in which the width direction is directed in the front-rear direction and a plurality of cross-sectional shapes aligned in the width direction are square. Flat left and right walls (131) and (132) (a pair of flat walls) facing each other, and both front and rear side walls (133) provided across the front and rear edges of both left and right walls (131) and (132) 134) and a plurality of partition walls that extend between the left and right walls (131) and (132) between the front and rear side walls (133) and (134) and extend in the length direction to partition adjacent refrigerant passages (130a) (135). It is preferable that the cross-sectional shape of the refrigerant passage (130a) is a square shape, and R at the corner of the cross-sectional rectangular refrigerant passage (130a) is 0.1 mm or less.

  The front side wall (133) has a double structure, and is integrally formed in a bulging shape on the right side from the front side edge of the left wall (131) and extends over the entire height of the heat exchange pipe (130). The inner side wall ridge (137) formed integrally with the right side ridge (137) on the inner side of the side wall ridge (136), and the left side ridge from the front edge of the right wall (132). The inner side wall convex strip (138) is formed. Note that both the inner and outer surfaces of the front side wall (133) are flat. The outer side wall ridges (136) are formed on the inner side wall ridges (137) (138) and the right wall (132) with the right end engaged with the right front edge of the right wall (132). It is brazed. Both the inner side wall convex strips (137) and (138) are abutted against each other and brazed. The rear side wall (134) is formed integrally with the left and right walls (131) (132), and both the inner and outer surfaces are flat. A protrusion (138a) extending in the longitudinal direction is integrally formed on the front end surface of the inner side wall protrusion (138) of the right wall (132) over the entire length, and the inner side wall protrusion (137) of the left wall (131). A concave groove (137a) that extends in the longitudinal direction and is press-fitted with a protrusion (138a) is formed over the entire length.

  The partition wall (135) is integrally molded in a leftward protruding shape from the right wall (132), and the partition wall projections (140) (141) that are integrally molded in a rightward protruding shape from the left wall (131). The partition wall projections (142) and (143) are formed by being butted against each other and brazed. On the left wall (131) and the right wall (132), two types of projections (140), (141), (142), and (143) for partition walls having different projecting heights are formed alternately in the front-rear direction. The partition wall projection (140) with a high protruding height on the left wall (131) and the partition wall projection (143) with a low projection height on the right wall (132) are brazed, and the left wall ( The protruding protrusions (141) for the partition wall having a low protrusion height in 131) and the protruding protrusions (142) for the partition wall having a high protrusion height in the right wall (132) are brazed. Hereinafter, the protruding ribs (140) and (142) for the partition walls having the high protruding heights of the left and right walls (131) and (132) are referred to as the first protruding ribs for the partition walls, respectively, and the protruding ribs for the lower partition walls (141) are also the same. Each of (143) is called a second partition wall projection. The first partition wall projections of the other walls (132) (131) extend in the longitudinal direction on the tip surfaces of the second partition wall projections (141) (143) of the left and right walls (131) (132). The groove (144) (145) into which the tip of the strip (142) (140) fits is formed over the entire length, and the first partition wall projection (140) (142) of the left and right walls (131) (132). The partition wall projections (140) (143) and (141) (142) are brazed in a state in which the leading end of each of the partition walls is fitted in the concave grooves (145) (144).

  In the heat exchange pipe (130) shown in FIGS. 16 and 17, each refrigerant passage (130a) excluding the two refrigerant passages (130a) located at both ends in the width direction, or all the refrigerant passages (130a). In some cases, two or more ridges extending in the length direction of the refrigerant passage (130a) may be formed on the inner peripheral surface.

  The heat exchange pipe (130) is manufactured using a pipe manufacturing metal plate (150) as shown in FIG. The metal plate for pipe production (150) is formed by rolling an aluminum brazing sheet having a brazing filler metal layer on both sides to form a flat left wall forming part (151) (flat wall forming part) and a right wall forming Part (152) (flat wall forming part), connecting part (153) for connecting left wall forming part (151) and right wall forming part (152) and forming rear side wall (134), and left wall forming part (151) and a ridge for the inner side wall which is integrally formed in a left-side raised shape from the side edge opposite to the connecting part (153) in the right wall forming part (152) and forms the inner part of the front side wall (133) (137) (138), and an outer side wall ridge forming part (154) formed by extending the side edge of the left wall forming part (151) opposite to the connecting part (153) outward. A plurality of partition wall projections integrally formed in a left-side raised shape from the left wall forming portion (151) and the right wall forming portion (152) at predetermined intervals in the width direction of the metal plate for pipe manufacture (150) Article (140) (14 1) (142) (143), and the first partition wall projection (140) of the left wall forming portion (151) and the second partition wall projection (143) of the right wall forming portion (152). ), And the second partition wall ridge (141) of the left wall forming portion (151) and the first partition wall ridge (142) of the right wall forming portion (152) are respectively connected to the connecting portion (153). It is in a position that is symmetric with respect to the center line in the width direction. A protrusion (138a) is formed on the front end surface of the inner side wall ridge (138) of the right wall forming portion (152), and a concave groove is formed on the front end surface of the inner side wall ridge (137) of the left wall forming portion (151). 137a) is formed respectively. Further, the second partition wall projections (141) and (143) of the left wall forming portion (151) and the right wall forming portion (152) are provided on the tip surfaces of the second wall forming portions (152) and (151). Concave grooves (144) and (145) into which the tip ends of the projections (142) and (140) for one partition wall are formed are formed.

  In addition, the aluminum brazing sheet clad with brazing material on both sides is subjected to a rolling process, and the side wall ridges (137) (138) and the partition wall ridges (140) (141) (142) (143) Are integrally molded, so that both side surfaces and front end surfaces of the side wall ridges (137) (138) and partition wall ridges (140) (141) (142) (143) and the second partition wall On the inner peripheral surface of the grooves (144) and (145) of the ridges (141) and (143) and on both the left and right sides of the left and right wall forming portions (150) and (151) and the outer side wall ridge forming portions (154) A brazing material layer (not shown) is formed.

  Then, the metal plate for pipe production (150) is sequentially bent at both side edges of the connecting portion (153) by roll forming (see FIG. 18 (b)), and finally folded into a hairpin shape to project the inner side wall. The ridges (137) and (138) are abutted with each other, and the leading ends of the first partition wall projections (140) and (142) are connected to the grooves (145) (145) of the second partition wall projections (143) and (141). 144) Fit into the groove, and press the protrusion (138a) into the groove (137a).

  Next, the outer side wall ridge forming part (154) is bent to be along the outer surface of the both inner side wall ridges (137) and (138), and its tip part is deformed to change the right wall forming part (152). To obtain a bent body (155) (see FIG. 18C).

  Thereafter, the bent body (155) is heated to a predetermined temperature, and the tips of the inner side wall ridges (137), (138), the first partition wall ridges (140), (142), and the second partition wall are used. While brazing the tip portions of the ridges (143) and (141), the outer side wall ridges (154), the inner side wall ridges (137) (138), and the right wall forming portion (152) The heat exchange pipe (130) is manufactured by brazing.

  FIG. 19 shows still another modification of the heat exchange tube.

  In FIG. 19, the heat exchange pipe (160) is a flat shape having a plurality of refrigerant passages (160a) aligned in the width direction with the width direction directed in the front-rear direction, and flat left and right walls (161) facing each other. The left and right walls between (162) and both the front and rear side walls (163) and (164) provided across the front and rear side edges of both left and right walls (161 and 162) and the front and rear side walls (163) and (164) (161) It includes a plurality of partition walls (165) that extend across the length and extend in the length direction and partition adjacent refrigerant passages (160a).

  The front side wall (163) has a double structure, and is integrally formed in a bulging shape to the right from the front side edge of the left wall (161) and the outer side wall ridge (166) extending over the entire height of the heat exchange pipe (160), Inside the side wall ridge (166), the inner side wall ridge (167) is integrally formed in a leftward protruding shape from the front side edge of the right wall (162) and covers the entire height of the heat exchange pipe (160). The rear side wall (164) has a double structure, and is integrally formed in a leftward protruding shape from the rear side edge of the right wall (162) and has an outer side wall ridge (168) extending over the entire height of the heat exchange pipe (160), Inside the outer side wall ridge (168), the inner side wall ridge (169) is formed integrally with the right side bulge from the rear edge of the left wall (162) and extends over the entire height of the heat exchange pipe (160). . The cross-sectional shape of both the inner and outer surfaces of the front and rear side walls (163) and (164) is an arc shape in which the central portion in the left-right direction protrudes outward. Further, the outer side wall projections (166) and (168) and the inner side wall projections (167) and (169) of the front and rear side walls (163) and (164) are brazed to each other.

  A corrugated partition wall forming portion (170) is formed between the tip of the inner side wall ridge (167) of the front side wall (163) and the tip of the inner side wall ridge (169) of the rear side wall (164). ) Are integrally formed. The partition wall forming part (170) includes a wave crest (171) brazed to the left wall (161), a wave bottom (172) brazed to the right wall (162), and a wave crest (171) and a wave bottom. (172) and a connecting portion (173) serving as a partition wall (165).

  Although not shown, the heat exchange pipe (160) is formed by bending a metal plate for pipe production made of an aluminum brazing sheet having a brazing filler metal layer on both sides to form a bent body. Outer side wall ridges (166) (168) and inner side wall ridges (167) (169), partition wall forming part (170) crest (171) and left wall (161), and wave bottom (172) And the right wall (162) are simultaneously brazed.

In the above embodiment, the evaporator according to the present invention is applied to an evaporator of a car air conditioner using a chlorofluorocarbon refrigerant, but is not limited to this, and is a compressor, a gas cooler as a refrigerant cooler, an intermediate heat exchange In a vehicle having an air conditioner, an expansion valve, and an evaporator and having a car air conditioner using a supercritical refrigerant such as a CO ₂ refrigerant, for example, an automobile, it may be applied to an evaporator of a car air conditioner.

1 is a partially cutaway perspective view showing an overall configuration of an evaporator according to the present invention. It is the vertical sectional view which abbreviate | omitted the intermediate part at the time of seeing the evaporator shown in FIG. 1 from back. It is the AA line expanded sectional view of Drawing 2 which omitted some. It is a cross-sectional view of the heat exchange tube of the evaporator shown in FIG. It is a disassembled perspective view of the part of the header tank for refrigerant | coolant in / out of the evaporator shown in FIG. FIG. 3 is a sectional view taken along line BB in FIG. 2. FIG. 7 is an enlarged sectional view taken along the line CC in FIG. 6. It is the DD sectional view taken on the line of FIG. FIG. 3 is a partially cutaway perspective view showing a right closing member and a joint plate of the refrigerant inlet / outlet header tank of the evaporator shown in FIG. 1. It is a disassembled perspective view of the part of the header tank for refrigerant | coolant turns of the evaporator shown in FIG. It is the EE sectional view taken on the line of FIG. It is a graph which shows the change of the discharged air temperature when the fixed capacity compressor of the car air-conditioner using an evaporator turns on and off. It is a cross-sectional view of the heat exchange pipe used for the evaporator of Examples 2-5 and a comparative example. It is a graph which shows the relationship between the cooling performance and the amount of liquid phase refrigerant remaining and the equivalent diameter. It is a graph which shows the relationship between the air_conditioning | cooling performance and the quantity of the remaining liquid phase refrigerant | coolants, and the number of refrigerant paths. It is a cross-sectional view showing a modification of the heat exchange tube. It is the elements on larger scale of FIG. It is a figure which shows the manufacturing method of the heat exchange pipe | tube shown to FIG. 16 and FIG. It is a cross-sectional view showing another modification of the heat exchange tube.

Explanation of symbols

(20): Evaporator
(21): Heat exchange core
(22): Header tank for refrigerant entry / exit
(23): Header tank for refrigerant turn
(24): Refrigerant inlet header
(25): Refrigerant outlet header
(30): Refrigerant inflow side intermediate header (first intermediate header)
(31): Refrigerant outflow side intermediate header (second intermediate header)
(34) (34A) (34B) (34C) (34D) (130) (160): Heat exchange tube
(34a) (130a) (160a): Refrigerant passage
(35): Heat exchange tube group
(36): Corrugated fin
(137) (138): Convex strip for inner side wall
(140) (141) (142) (143): Projection for partition wall
(150): Metal plate for pipe manufacturing
(151): Left wall forming part (flat wall forming part)
(152): Right wall forming part (flat wall forming part)
(153): Connecting part
(341) (131) (161): Left wall (flat wall)
(342) (132) (162): Right wall (flat wall)
(343) (133) (163): Front side wall
(344) (134) (164): Rear side wall
(345) (135) (165): Partition wall
(167) (169): Convex for inner side wall
(170): Partition wall forming part
(171): Wave peak
(172): Wave bottom
(173): Connecting part
(346): Projection

Claims (23)

A heat exchange pipe that is flat and has a plurality of passages arranged in the width direction,
A heat exchange tube that satisfies the relationship of 0.558 ≦ A ≦ 1.235, where A (pieces / mm) is the value obtained by dividing the number of passages by the width in the front-rear direction. A heat exchange pipe that is flat and has a plurality of passages arranged in the width direction,
A heat exchange tube that satisfies the relationship of 0.35 ≦ Dh ≦ 1.0 when the equivalent diameter is Dh (mm). The heat exchange pipe according to claim 1 or 2, wherein a ridge extending in the length direction of the passage is formed on an inner peripheral surface of each passage excluding two passages located at both ends in the width direction among all the passages. The heat exchange tube according to claim 3, wherein the number of ridges formed on the inner peripheral surface of each passage is two or more. 2. The cross-sectional shape of each passage excluding two passages located at both ends in the width direction of all the passages is a square shape, and the corner portion R of the cross-sectional square passage is 0.1 mm or less. 2. The heat exchange tube according to 2. Two flat walls that are parallel to each other, both side walls that are provided across both side edges of both flat walls, and that are provided between both side walls so as to straddle both flat walls and extend in the length direction of both flat wall portions. The heat exchange pipe according to any one of claims 1 to 5, wherein the heat exchange pipe is formed of an extruded shape member provided with a partition wall that partitions the matching passages. Two flat walls parallel to each other, both side walls provided across both side edges of the both flat walls, and provided between both side walls so as to straddle both flat walls and extend in the length direction of both flat wall portions. And a partition wall that partitions the matching passages,
Two flat wall forming portions that form a flat wall, a connecting portion that connects both flat wall forming portions and one side wall, and a side edge opposite to the connecting portion in each flat wall forming portion, Side wall ridges that are integrally provided so as to protrude from the flat wall forming portion and that form the other side wall, and are integrally provided on each flat wall forming portion so as to protrude in the same direction as the side wall ridges. One metal plate provided with a plurality of partition wall ridges is formed by being bent into a hairpin shape at the connecting portion, the side wall ridges are butted together and brazed to each other, and at least The heat exchange pipe according to any one of claims 1 to 5, wherein a partition wall is formed by the partition wall protrusions of any one of the flat wall forming portions. The heat exchange pipe according to claim 7, wherein the partition wall is formed by abutment of the projections for the partition walls of the two flat wall forming portions and brazing each other. 9. A concave groove into which the tip of the other partition wall ridge is fitted is formed on the tip surface of one of the partition wall ridges of the two partition wall ridges forming each partition wall. The heat exchange tube as described. Two flat walls parallel to each other, both side walls provided across both side edges of the both flat walls, and provided between both side walls so as to straddle both flat walls and extend in the length direction of both flat wall portions. And a partition wall that partitions the matching passages,
For a side wall formed by bending one metal plate, one side wall is formed so as to project to the other flat wall side, continuing to one side edge of one flat wall, and facing the refrigerant passage Having a ridge, the other side wall is formed to be continuous with the other side edge of the other flat wall and project to the one flat wall side, and has a ridge for the side wall facing the refrigerant passage, A corrugated partition wall forming portion is integrally formed between the tip of the side wall ridge on the side wall and the tip of the side ridge on the other side wall, and the partition wall forming portion is one flat wall. The heat exchange tube according to claim 1 or 2, comprising a wave crest portion brazed to each other, a wave bottom portion brazed to the other flat wall, and a connecting portion that connects the wave crest portion and the wave bottom portion and serves as a partition wall. It has a plurality of flat heat exchange tubes with the width direction facing in the front-rear direction and spaced in the left-right direction and extending in the up-down direction, and the heat exchange tubes have a plurality of refrigerant passages arranged in the width direction. An evaporator,
An evaporator that satisfies the relationship of 0.558 ≦ A ≦ 1.235, where A is a value obtained by dividing the number of refrigerant passages of the heat exchange tube by the width in the front-rear direction of the heat exchange tube. It has a plurality of flat heat exchange tubes with the width direction facing in the front-rear direction and spaced in the left-right direction and extending in the up-down direction, and the heat exchange tubes have a plurality of refrigerant passages arranged in the width direction. An evaporator,
An evaporator that satisfies the relationship of 0.35 ≦ Dh ≦ 1.0, where Dh is the equivalent diameter of the heat exchange tube. 12. A ridge extending in the length direction of the refrigerant passage is formed on the inner peripheral surface of each refrigerant passage excluding two refrigerant passages located at both ends in the width direction of all the refrigerant passages of the heat exchange pipe. Or the evaporator of 12. The evaporator according to claim 13, wherein the number of ridges formed on the inner peripheral surface of each passage of the heat exchange pipe is two or more. The cross-sectional shape of each refrigerant passage excluding two refrigerant passages located at both ends in the width direction of all the refrigerant passages of the heat exchange pipe is square, and R at the corner of the transverse refrigerant passage is 0. The evaporator according to claim 11 or 12, which is 1 mm or less. A heat exchange pipe is provided between two flat walls parallel to each other, both side walls provided across both side edges of the two flat walls, and the length of both flat walls between both side walls. The evaporator according to any one of claims 11 to 15, wherein the evaporator is formed of an extruded shape member that includes a partition wall that extends in a direction and partitions adjacent passages. A heat exchange pipe is provided between two flat walls parallel to each other, both side walls provided across both side edges of the two flat walls, and the length of both flat wall portions provided between both side walls. A partition wall extending in the direction and separating adjacent passages,
The heat exchange pipe has two flat wall forming portions that form flat walls, a connecting portion that connects both flat wall forming portions and forms one side wall, and a side opposite to the connecting portion in each flat wall forming portion. Side wall ridges that are integrally provided to protrude from the flat wall forming portion and that form the other side wall, and that each flat wall forming portion protrudes in the same direction as the side wall ridges. A single metal plate having a plurality of partition wall projections provided integrally is bent into a hairpin shape at the connecting portion, and the side wall projections are butted together and brazed to each other. The evaporator according to any one of claims 11 to 15, wherein the partition wall is formed by a projection for the partition wall of at least one of the flat wall forming portions. The evaporator according to claim 17, wherein the heat exchange pipe is formed by brazing the partition wall with the partition wall protrusions of the flat wall forming portions being abutted with each other. 19. A concave groove in which the tip of the other partition wall ridge is fitted is formed on the tip surface of one of the partition wall ridges of the two partition wall ridges forming each partition wall. The described evaporator. A heat exchange pipe is provided between two flat walls parallel to each other, both side walls provided across both side edges of the two flat walls, and the length of both flat wall portions provided between both side walls. A partition wall extending in the direction and separating adjacent passages,
The heat exchange tube is formed by bending one metal plate, and one side wall is formed to be continuous with one side edge of one flat wall and project to the other flat wall side, and the refrigerant passage A side wall ridge that faces the refrigerant passage and has a side wall ridge facing the inside, the other side wall being connected to the other side edge of the other flat wall and projecting to the one flat wall side. And a corrugated partition wall forming portion is integrally formed between the tip of the side wall ridge on one side wall and the tip of the side wall ridge on the other side wall. 16. A wave crest portion brazed to one flat wall, a wave bottom portion brazed to the other flat wall, and a connecting portion that connects the wave crest portion and the wave bottom portion and serves as a partition wall. The evaporator as described in any one of them. A refrigerant inlet / outlet header tank having a refrigerant inlet header portion and a refrigerant outlet header portion arranged side by side in the front-rear direction, and a first refrigerant tank arranged opposite to the refrigerant inlet header portion and spaced below the refrigerant inlet / outlet header tank. A refrigerant turn header tank having a second intermediate header portion facing the first intermediate header portion and the refrigerant outlet header portion and communicating with the first intermediate header tank, and a heat exchange core portion formed between the two header tanks The heat exchange core section is arranged in the length direction of both header tanks at intervals, and the heat exchange pipe group consisting of a plurality of heat exchange pipes whose both ends are connected to both header tanks and the adjacent heat It consists of fins arranged between the exchange pipes, and two or more heat exchange pipe groups are arranged side by side in the ventilation direction between both header tanks, and the refrigerant inlet header part, the first intermediate header part, and Evaporator according to any one of claims 11 to 20 heat exchange tubes of at least one heat exchange tube group are the refrigerant outlet header section and the second intermediate header section are connected. A refrigeration cycle comprising a compressor, a condenser, and an evaporator, wherein the evaporator is an evaporator according to any one of claims 11 to 21. A vehicle on which the refrigeration cycle according to claim 22 is mounted as a car air conditioner.

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